Gear Cutting Machine.
Year: 1895

page_text: Date of Application, 8th Jan., 1895-Accepted, 4th May, 1895
Gear Cutting Machine.
I, LUCIUS ERSKINE WHITON, of 59 Howard Street in the City and County
of New London, State of Connecticut, United States of America, Manufacturer,
do hereby declare the nature of this invention and in what manner the same is to
be performed, to be particularly described and ascertained in and by the following
statement :-
The immediate object of this invention is to produce a gear cutter which will be
entirely automatic, whose various movements shall be so timed, relatively to each
other, that the greatest possible economy of time shall result and which will cut,
with equal facility, spur or bevel gears yet, notwithstanding the variety and range
of work performed, the mechanisms employed are not complex. A particularly
valuable feature of my gear cutting machine should be noted in the fact that its
various movements not only follow each other, automatically, in practical and proper
sequence but that each of said movements is controlled, and depended upon, the
completion of the next preceding movement so that the failure of either of the several
elementary mechanisms to work properly will serve to prevent the starting and
operation of all the succeeding mechanisms, thus avoiding all chance of mutilated
blanks or otherwise spoiled work.
A further important object of my invention is to provide a machine in which the
several mechanisms are all positively driven thus eliminating the danger of imperfect
action resulting from the use of frictional devices, and avoiding the constant waste
of power entailed by such devices as well as the necessity of careful and frequent
adjustment.
To explain my invention most clearly I have provided the annexed drawings,
in which:
Fig. 1, is a front side elevation of a gear cutting machine embodying my
invention; and
Fig. 2, is a rear side elevation of the same.
In these views the head (52) (upon which are mounted the carriages that support
the cutter-shaft) is an integral part of the machine bed but in Fig. 3 said head is
shown as cast separately and bolted to the bed.
Fig. 4, is a plan view of said gear cutter; and
Fig. an end elevation of the same with the machine-legs removed. This
figure also shows broken away the casing of what I term a "spacing box," which
box contains the mechanism that controls and actuates the spacing of the gear teeth.
Fig. 6, is a rear side elevation of the head that supports the cutter shaft
carriages and also illustrates, in section a portion of the bed and of an extension of
said bed which I term the "feed box," in which box is located the mechanism
that controls the traversing movements of the cutter.
Fig. 7 is a front side elevation of said head and has also a sectional view of
the spacing box, illustrating particularly the mechanism by means of which the
downward feed of the cutter shaft is arrested and the return feed set in operation.
Figs. 8 and 9 are views taken within said spacing box and described in detail
hereinafter.
Fig. 10 is a vertical, sectional, view of the head 52 taken on line x-x of Fig. 4,
disclosing the feed-screw which moves the carriages that support the cutter shaft.
Fig. 11 is an elevation of the upper portion of the head 52, as viewed from the
left hand end of Fig. 1, showing the projecting end of a screw-shaft that may be

page_text: rotated (by means of a suitable wrench) to raise or lower the initial carriage of
the train of carriages that support the cutter shaft; and
Fig. 12 is an elevation of the head 52 as viewed from the right hand side of
Fig. 1, showing mounted thereon said initial carriage and also the next of the train.
Figs. 13, 14 and 15 are, respectively, cross-sectional views on lines a-x, y-y
and 2-2 of Fig. 10 (the carriage 76 being removed in Fig 14); and
Fig. 16 is an elevation of a portion of the rear (inner) side of head 52 illustrating
the manner in which said head is chambered to receive and support a spiral
gear 108 mounted upon a vertical shaft that controls the cutter-feed.
Fig. 17 is a view of a portion of head 52 similar to that shown in Fig. 10,
illustrating a screw (for hand use) by means of which the initial carriage and its
various supports may be raised or lowered independently of the automatic feeding
devices.
Fig. 18 is a cross-sectional view of the machine bed having mounted thereon the
revoluble spindle that supports the gear-blank during the operation of cutting and
also illustrating worm-gear and shaft connections for revolving said blank-supporting
spindle.
Fig. 19 is a detached plan view of said revolving spindle and of the carriage
upon which it is mounted.
Fig. 20 is a plan view of the revolving blank support, its worm and worm-shaft
and, also of a screw-shaft by means of which said blank support may be adjusted
upon the machine bed within the limits of its ways.
Fig. 21 is a side elevation of the upper portion of the hollow blank-supporting
spindle; and
Fig. 22 is a plan of a ring secured to said spindle for a purpose hereinafter
explained.
Fig. 23 shows a portion of the right hand end of the machine bed of Fig. 1; and
Fig. 24 is a plan of substantially the same parts.
Fig. 25 shows a cross section of a portion of the rear side of the machine bed
having connected therewith certain elements of the mechanism that drives the
cutter-shaft.
Figs. 26 and 27 are side and end views of a clutch shifting mechanism that may
be operated by hand to stop the cutter-feed shaft; and
Fig. 28 is a detached view of an eccentric and an arm operating therewith
forming parts of said clutch-shifting mechanism.
Fig. 29 is an end view of the clutch section (121) that controls the cutter feeding
devices and also shows an encircling ring that is used to shunt said clutch section
into and out of operative engagement with its companion section.
Fig. 30 is an enlarged view of the front face of the "spacing box" which is, in
effect, an extension of the bed 50; and
Fig. 31 is a similar view of the rear face of the "spacing box."
Fig. 32 is a view of a cross-shaft 128 located in the "spacing box" and having
mounted thereon certain devices for releasing at stated times the mechanism that
partially revolves the blank supporting spindle to "space" for the next tooth.
Fig. 33, illustrates, by end and edge views, the clutch-operating ring referred to
in Fig. 29 and also a rocking segment used to shunt said ring.
Fig. 34 is a detached view of the pawl 170 and ratchet 167 of Fig. 9.
Fig. 35 shows, detached, one of the gears (139) and a telltale which extends
outward, through the wall of bed 50 to indicate the positions of the said gears
relatively to the spline that locks them to the cam shaft.
Fig. 36 illustrates certain mechanism provided to shift said spline in its seat to
lock either of the gears to the cam shaft.
Figs. 37 and 38 are face and sectional views of a graduated disc or index used
in connection with the blank spacing mechanism; and
Fig. 39 is a plan view of the clainping device of the said index.
Fig. 40 shows, detached from their bearings and other supports, several of the
most important shafts and their connections.

page_text: Figs. 41, 42 and 43 illustrate a certain escapement that "times" and controls
the cutter-feeding mechanism; and
Figs. 44 and 45 illustrate certain mechanism for automatically stopping the
machine upon the completion of a gear.
Figs. 46 and 47 show side and front elevation of the upper end of the lever-
arm 178 showing the bell-hammer 2081 pivoted thereto.
In these drawings 50 indicates the bed of my gear cutting machine, 51 its
supporting legs and 52 an upwardly extending head located at one end of bed 50
and, preferably, formed integral therewith as in Fig. 2, although it may be cast
separately and bolted to the bed, as in Fig. 3.
The upper portion of bed 50 is formed with parallel ways 53 upon which is
mounted to slide a carriage 54 (shown on a larger scale in Figs. 18 and 19); said
carriage having a downwardly extending shell 55 which is bored to receive a
hollow spindle 56. Said spindle is held against end wise movement in one direction
by an annular enlargement 57 seated in the counter-bored carriage 54 and in the
opposite (upward) direction by a worm gear 58 whose hub abuts the lower end of
the shell 55. Gear 58 is secured to and rotates with the spindle 56. Secured to
the lower end of said shell is a shield 59 having a lateral extension 60 that is bored
to receive a shaft 61 and counterbored to provide a chamber in which is located a
worm 62 that meshes with gear 58 and, under certain conditions, is brought into
service to partially rotate the worm gear. 63 denotes a thimble or bushing screwed
into the otherwise open end of the extension 60 forming an abutment for one end
of worm 62 which latter is splined upon shaft 61 and is free to slide thereon.
Shaft 61 is located at what I consider the front side of the machine, being the
side at which the operative naturally stands and is journalled in bearings 64 bolted
to bed 50.
Referring now particularly to Figs. 18 and 20, it will be seen that the shell 55
has screwed to it a threaded bracket 65 within which is mounted a screw 66
journalled in the machine bed 50 having one end projecting beyond said bed as in
Figs. 1, 2, 23 and 24. This projecting end is shaped to receive a wrench or, if
preferred, may be provided with a hand wheel by means of which the screw 66 may
be rotated to move the connected shell 55, carriage 54 and the blank-supporting
spindle 56, along the ways 53. Screw 66 as here shown has no connection with the
various automatic mechanisms of my machine but, per contra, is operated only by
hand whenever it may be necessary to vary the position of the spindle 56, relatively
to the cutter, to accommodate gear-blauks of greater or lesser diameter.
exposed end of screw 66 has secured to it a collar 67 that is graduated, as
shown in Fig. 23, so that partial revolutions of said screw may be accurately made
to vary the depth of the teeth of the gears, by slightly moving the blank toward or
away from the cutter.
The
Referring now to Figs. 1, 2, 4, 5, 6 and 10 to 17 it will be seen that the face of
the head 52 is formed with dove-tail ways in which a carriage 68 may slide and I
also provide in connection with said carriage a screw 69 that is journailed in head 52
and engages a threaded bracket 70 extending laterally from carriage 68 as best seen
in Figs. 13 and 17.
The lower front portion of carriage 68 is formed with perforated ears 71 in
which is journalled a short shaft 72 whose ends project like trunnions and support
frames 73 and 74 that are bolted, or otherwise secured to the sides of a plate 75,
which latter is thus hinged to carriage 68 and adapted to be swung on the shaft 72
to vary the inclination of plate 75 relatively to the head 52 and bed 50, as seen in
Fig. 6. The exposed face of plate 75 is formed with ways upon which a
carriage 76 is fitted to slide, said carriage being provided with a threaded
extension 77 that is engaged and controlled by a screw shaft 78 journalled in the
plate 75 at top and bottom of the latter. The carriage 76 is formed with
transverse ways in which is fitted a carriage 79 that may thus be adjusted, a
limited distance, in a direction at a right angle to the movement of its supporting
carriage 76. This transverse carriage may be firmly clamped, after adjustment, by

page_text: means of a set screw 80 that projects outward through a slot in carriage 76 (see
Fig. 13).
The hinged frames 73 and 74 are each formed with slotted arc-shaped
extensions 81-82 that pass rearward alongside the carriage 68 and head 52, when
the plate 75 and its attachments are swung to a vertical position, as in Fig. 7. By
means of screws 82', located in the slots of extensions 81-82 and tapped into
carriage 68, the plate 75 may be firmly clamped at any inclination within the
limits of the arc-shaped slots.
Journalled in the transversely adjustable carriage 79 is a shaft 83 one of whose
ends projects sufficiently to receive a suitable mill or cutter for use in cutting the
gear teeth. This projecting end is shown most clearly in Fig. 4 but is thought
unnecessary to show a cutter attached thereto. Said cutter, when secured upon
shaft 83, should register perfectly with the center of the mandrel opening in the
spindle 56 and should there be any variation it may be quickly corrected by easing
back the set screw 80 and sliding the carriage 79 in its ways until the desired
adjustment is attained.
I will now proceed to describe the mechanism which revolves the shaft 83 and
the cutter mounted thereon. In the rear portion of the side walls of head 52
is journalled a shaft 84 which constitutes the prime mover of my machine and which
bears a pulley 85 that may be driven from any convenient countershaft. Upon the
rear end of shaft 84 is a bracket arm drilled to provide two journal bearings 86
and 87 that are at a right angle to each other.
One of said bearings 86 supports a bevel gear 88 and the companion bearing 87
is mounted upon the projecting end of shaft 84, just inside a bevel gear 89 that
may thus mesh with the gear 88 and drive the latter when the shaft 84 is in
revolution.
Within the bevel gear 88 is a shaft 90 that is splined to slide longitudinally
therein and which bears upon one end a small bevel gear 91 that meshes with a
larger gear 92 secured to the end of the cutter-shaft 83 in such manner that, when
the initial shaft 84 is started, rotary motion is imparted to the cutter shaft, as will
be best understood by reference to Fig. 4 of the drawings. The end of shaft 90
nearest gear 91 is supported in a journal bearing 93 secured to an arm 94 whose
adjacent end is swivelled on the movable carriage 76. The other end of said
arm 94 extends parallel with shaft 90 and is slotted, as at 95, to straddle the
shaft, 84. This manner of supporting said arm permits free endwise movement and
also holds it and the shaft 90 parallel.
Whenever it is necessary to vary the inclination of the plate 75 to cut bevel or
mitre gears, the splined shaft 90 and its supporting arm 94 readily adjust themselves
to such changes as also to all changes of position of cutter carriage 76, yet the
several gears of the train always remain in mesh.
66
"
I will now describe the mechanism employed to feed the cutter and its supports
downward by a slow and regular movement to cut a tooth, and then upward by a
quick return movement of its point of starting, calling particular attention to
Figs. 2, 4, 5 and 6. Fixed upon the initial shaft 84, between the side walls of
head 52, is a gear 95 that meshes with and drives a like gear 96 on a shaft 97 that
is also journalled in said side walls.
Upon the projecting end of shaft 97, at the rear side of the machine, is a small
spur gear 98 that meshes with and drives a larger gear 99 which, in turn, drives a
small gear 100 on a short shaft 101 journaled in the rear wall of bed 50 and in a
bracket 102 secured to said bed (see Fig. 25).
This short shaft bears upon its inner end, inside the machine bed, a bevel
gear 103 that drives a similar gear 104 mounted loosely on a shaft 105, that is
parallel with the machine bed and extends to a point beneath the carriage 68 on
head 52, where it terminates in a loosely mounted mitre gear 106 that meshes with
a similar gear 107 splined on a vertical shaft 68°. The gear 106 is, ordinarily,
connected with shaft 105 by a clutch 190-191 illustrated in Fig. 40 and described
hereinafter.

page_text: Whenever the gear 106 is set in revolution, motion is impartel to the shift 68
which is journalled in the lower end of carriage 63 an! bears a spiral gear 103 (see
Fig. 16) that meshes with an I drives a corresponding gear 109 mounted upon the
shaft 72 already described.
While I have shown and described spiral gearing for transmitting motion from
the shaft 68 to the hinge-shaft 72 I do not wish to be confined to the use of such
spiral gears as mitre gears could be successfully substituted therefor.
Upon the shaft 72 is a mitre gear 110 that meshes with a like gear 111 on the
screw-shaft 78, also hereinbefore described, and it will now be understood that -
when rotary motion is given to the splined shaft 68" a corresponding motion will be
imparted, through the described train of gearing to said screw-shaft 78 which will
at once cause the carriage 76 and the connected cutter-shaft carriage to travel
upward or downward according to the direction of rotation of said shaft 63ª and
it will also be understood that by reason of the location of the mitre-gear 110 on
the shaft 72 (which forms the pintle of the hinged plate 75) the gears 110 and 111
will remain in operative engagement whether the cutter and its supports are in the
vertical position of Figs. 1, 2 and 7 or inclined, as in Fig. 6, to cut bevel gears.
The shaft 78 is here shown cut as a single thread of ordinary pitch but, when a
quick return movement of the carriage is to be desired, said screw-shaft may be
cut with a double or treble thread and of increased pitch.
In order to control both the upward and downward movements of the cutter, to
obtain the most satisfactory and economical results it is desirable that the down-
ward, or cutting, movement shall be very slow but that the upward, or return,
movement shall be very rapid and these results I am able to attain by providing two
separate driving mechanisms for the shaft 105 of which the described bevel
gears 103-104 constitute the quick return driving mechanism. The slower, or feed,
movement is imparted to said shaft 105 by a train of gearing best seen in Figs. 2, 6
and 40.
The shaft of gear 99 (indicated by 99*) bears also a small gear 112 in mesh with
a gear 113 that is adjustably mounted and serves as an intermediate between the
said gear 112 and a gear 114 on a short shaft 115 journalled in the "feel box
secured to the bed 50.
"
Secured upon said shaft 115 is a worm 116 that engages and drives, at a very
slow rate, a worm gear 117 loosely mounted on the shaft 105.
"
Through the train of gearing 112, 113 and 114 said worm gear 117 is caused to
revolve in a direction opposite to that of the "quick return
gear 104. The
latter named gear (104) is formed with a long hub which revolves in a shell 118
that is fixed in the bed 50. The confronting ends of gear 104 and worm gear 117
are provided with notches or depressions that may be engaged by corresponding
projections 120 at the ends of a sliding clutch-collar 121 that is splined to
shaft 105. I prefer to provide several depressions in the shell and worm gear and
but two projections 120 at each end of the clutch collar and I also by preference
form the said projections as spring-pressed bolts, as clearly seen in Fig. 6 of the
drawings so that, when the clutch-collar is shunted on shaft 105 to interlock with
either of the loose clutch sections, if the projections and notches fail to register, the
projecting bolts may be forced back for an instant and ride around until they
coincide with their respective notches when the springs will force them ahead into
said Lotches. By thus providing a splined sliding clutch section to lock with the
worm gear 117 at one end or with the bevel-gear 104 at the opposite end I am
able to lock either of said gears to shaft 105 and thus rotate said shaft in opposite
directions and at different speeds.
To thus slide the clutch section 121 I have provided thereon a ring section 122
(see Figs. 6, 29, 33, and 40) which has secured to one side a short rack 123 that is
parallel with the desired movement of the clutch section 121.
In order to carry into effect one of the essential principles of my complete
machine (namely the dependence of each movement upon the completion of the
last preceding movement) it is necessary that the sliding clutch-section 121 be

page_text: given three distinct steps or movements; that is to say (1) a movement in one
direction to lock with and be revolved by the worm gear 117 to produce the slow
feed for the cutter, (2) a movement in the opposite direction to lock with the bevel
gear 104 to set shaft 105 in operation in the opposite direction at increased speed
and (3) a limited return movement which shall leave said clutch section in a neutral,
.position between said gears so that shaft 105 and the cutter feed shall be at rest
during the time required to partially revolve the blank that is being cut,
preliminary to cutting the next tooth.
To thus control the sliding clutch section, and to produce these three described
movements, I have provided novel mechanism which will be best understood if
reference is made to Figs. 5, 7, 8, 32, 33, 40, 41, 42 and 43. In Figs. 7, 8 and 40
will be seen the shaft 99, extending nearly across the machine and terminating
with a mitre gear 124 that meshes with and drives a like gear 125 mounted loosely
upon a shaft 126, said gear 125 having an enlarged extension 127 that forms the
loose half part of a clutch whose companion part 127' is fixed on the shaft 126. The
clutch section 127 is kept in constant revolution but the companion section and its
shaft 126 are only moved at such times as the clutch sections may be locked
together. 128 indicates a rock-shaft journalled within the "spacing box
and
having at one end a gear segment 129 that meshes with the described rack 123 on
the clutch ring 122 (see Fig. 33), in such manner that the rocking of shaft 128
will serve to slide said collar and its connected clutch section: the length and
direction of movement of said clutch, being determined by the movements of
shaft 128.
"
The mitre gear 124 has an extended hub 124* which constitutes the driving half
of an intermittently acting clutch similar to 127 and 1271 on shaft 126 previously
referred to.
Shaft 99 has also loosely mounted thereon a gear 129' which meshes with and
at certain times drives a similar gear 130 hung at a point midway the shaft 99"
and 128 and this last named gear bears upon one face a roll 131 which is eccentric
to said gear and lies within an opening 132 in a plate 133 secured to shaft 128.
Whenever gear 130 is caused to rotate, the roll 131 engages one wall of the
opening 132 thus rocking shaft 128 and moving the feeding clutch 121 into
engagement with the "quick return "
gear 104.
In Fig. 42 the plate 133 is shown
in full lines thus moved, the eccentric roll having passed around out of contact
with the wall of opening 132. Continued movements of said roll at the proper
time brings it into contact with the opposite wall of the opening which is of such
width that said roll moves the plate back to the position shown in full lines in
Fig. 43 rocking shaft 128 sufficiently to move the feed clutch into its neutral
position.
The third step, necessary to rock the shaft 128 into the position shown in full
lines in Fig. 41 and thus throw into clutch the slow feed movement of the cutter,
is not brought into action until the blank-spacing mechanism has completed its
work, but as this third step relates particularly to the feed mechanism just set
forth it is thought best to describe it here. Said third step is obtained through a
cam 134 on a shaft 135 that is parallel with shaft 1:6 but in a lower plane (see
Figs. 5 and 40). This cam 134 engages at the proper time a roll 136 hung in a
radial arm 137 fixed on shaft 128 and forces said arm downward sufficiently far
to rock the shaft 128 and slide the clutch section 121 into operative engagement
with the worm gear 117 thus starting the slow feed mechanism of the cutter.
Figs. 7 and 40 best illustrate the manner of driving the cam shaft 135.
Shaft 126, which has already been referred to, bears upon its inner end one or
more gears 138 of different diameters that mesh with like gears 139 on the cam
shaft 135.
Gears 138 are fixed on their shaft but the gears 139 are loosely mounted and
are only connected with their shaft 135 by a sliding spline 140 whose exposed
portion is formed as a continuation of shaft 135 and cut with annular grooves to
form a rack. 141 that may be engaged by a pinion 142 on a short shaft or stud 143

page_text: arranged to both slide and revolve in the wall of bed 50. The outer end of
shaft 143 is provided with an operating handle or knob 144 by means of which
said shaft may be partially rotated to slide the spline-rack 140 and so lock either
of the gears 139 to the cam-shaft 135 the other gears on said shaft meanwhile
running idly. To lock the shaft 143 after adjustment I have provided in the basa
of knob 144 a pin 145 that may enter either of several holes in bed 50 and to retain
said pin in the holes I have placed a spring 146 on shaft 143 between said bed and
the spur gear 142, as in Fig. 36. When it is necessary to slide the spline 140 the
knob 144 is first grasped and drawn outward to release the pin 145. Shaft 143 is
then rotated to move the spline, the holes for pin 145 serving to show when the
proper adjustinent has been reached. When knob 144 is released the spring 146
draws shaft 143 inward and the pin 145 then locks the shaft against accidental
displacement.
The gears 138-139 are of such relative sizes that the speed of the cam shaft 135
may be varied by bringing into use the different gears and, thus, the time allowed
for the revolution of shaft 126, and its connected mechanism, for shifting the gear
blank to space for the next tooth, may be correspondingly varied, as more fully
set forth hereinafter.
This is desirable for the reason that, in some distances, it is necessary to allow
more time for the blank-spacing mechanism to act before starting again the cutter-
feeding devices.
It will be seen by reference to Figs. 7 and 35 that the gears 139 are each turned
down to provide a hub or boss 146¹ that is flattened at one side, as at 147, said
flattened portion being so located relatively to the spline 140 that when the spline-
seats in all of the gears 139 are brought into coincidence with the spline this
flattened portion faces the front wall of bed 50 and I have located in said bed
spring-pressed bolts 148 whose inner ends are flattened to enter between the
gears 139 and ride upon the circumferential edge of the hubs 146' and whose outer
ends project slightly through bed 50, as seen in Fig. 1, to serve as indicators to
show when gears 139 are in proper position to allow the spline to be moved by the
knob 144, as above described.
"
Upon the end of shaft 126 that projects through the "spacing box is a
gear 149 that is mounted upon said shaft and clamped in place by a nut 150. This
gear 149 meshes with a gear 151 mounted on a stud 152 that is adjustably secured
to an arm 152 (see Fig. 31). Gear 151 meshes with a gear 153 on the end of the
spacing shaft 61 and, by suitable changes in the train of gearing, the speed of
shaft 61 relatively to its driver 126, may be varied at will.
Shaft 61 I have already described as located at the front side of the machine
(see Figs. 1, 4, 16 and 20) and as having a worm 62 that meshes with a worm-
gear 58 controlling the rotary motion of the spindle 56 and of a gear blank held
therein. Whenever the train of gearing 149, 151 and 153 is set in motion shaft 61
is correspondingly moved. Worm 62, being splined on said shaft, then partially
rotates the worm gear 58 and thus moves the gear blank around a suitable distance
to receive the next cut.
The revolution of shaft 61 is necessarily very slight as it is desired ordinarily
to feed the gear blank around only a distance equal to one tooth.
I have now described in a géneral way the several shafts and connecting
mechanism for revolving the cutter shaft, for feeding said cutter shaft and returning
it to its starting point, for adjusting the blank supporting carriage on its ways
and for revolving said blank supports.
I will now explain in detail various clutches and escapements which control the
starting and stopping of the said shafts and which, as a rule, are dependent for
their action upon the completion of some important preceding movement.
If reference made to Figs. 1, 4, 5 and 7 it will be seen that the cutter shaft
carriage 76 has secured to one side a bracket 76' that is adapted to slide on a
rod 154 loosely fitted at its upper end in a stand 155 secured to the plate 75 and
=

page_text: is connected at its lower end with a crank-arm 156 hung on the projecting end
of the hinge pintle 72.
Said arm 156 is also formed with a plate 157 having an arc-shaped slot in
which is adjustably clamped one end of a rod 158 whose other end is connected
with the upper end of a lever 159, that is fulcrummed on a stud or screw 160
projecting from the head 52. Rod 154 has adjustably mounted thereon two
collars 154-154ª which, in practice are so adjusted on rod 154 that they will be
engaged by bracket 761 just as the cutter-shaft carriage is about to complete its
movement in either direction. Continued movement of said carriage then serves
to slide rod 154 in the direction of the moving carriage. The lower end of the
lever 159 is shaped substantially like the fork of an anchor escapement, the arms
of which terminate with inwardly projecting ends 1591-159 and immediately in
the rear of said fork is a plate 159b that projects downward from the arm 159
a considerable distance, as seen in Figs. 7, 41 and 42. The escapement fork is
here illustrated as a curved rib formed upon the face of the plate 15yb and integral
therewith.
In Fig. 42 it will be seen that plate 159 lies in an annular groove 129 and that
its longer end lies between two projecting ends 1331 and 133 of the plate 133.
When the lever arm 159 is rocked in either direction this projecting end of the
plate 159 acts by engagement with one of the projections 133-133" to rock the
shaft 128 a sufficient distance to disengage the clutch points 120 from the worm-
gear 117, or quick return gear 104 as the case may be, and thus stop the cutter-shaft
carriage. The movement of plate 159b serves also to release the clutch mechanism
of gear 1291 permitting it to make a partial revolution thus setting in motion
gear 130 and, by means of eccentric roll 131, to continue the rocking motion of
shaft 128 hegun by plate 159b as above described.
Fig. 40 shows clearly the shaft 99* having fixed thereon the mitre gear 124 and
also the loosely mounted gear 129' before described. Gear 129¹ has a hub 129
that extends toward and abuts the hub of the mitre gear 124 and is formed with
the annular groove 129b.
When my machine is assembled the plate 159 of lever 159 lies in said groove 129h
(see Fig. 42) and the escapeinent points 159' and 159 overlap the hub 129ª and
are adapted to engage alternately (when lever 159 is rocked) a latch 161 that
projects radially from said hub 129. The confronting ends of hubs 129 and 124
are peculiarly formed to provide a clutch that may be brought into use whenever
it is desired to lock together said hubs to set in motion the gear 129' and the
gear 130. Fig. 41 illustrates most effectually the construction of said clutch. The
hub 124 is recessed in such manner that one or more inward projections 124¹ are
provided, the inner edges of said projections being concentric with the hub. In
Fig. 41 the recessed rim of hub 124 that bears the said inward projections is shown
in section and immediately in its rear is seen the end of the hub 129 which has
pivoted therein near one edge the radial latch 161 above referred to.
The body
portion of said latch is substantially circular and is seated in a corresponding recess
in the end of hub 129ª the radial arm of said latch projecting ontward beyond
the circumference of the hub.
The circumferential opening or slot through which the latch end projects is
enlarged in one direction so that the projecting end of the latch may at times be
rocked and folded down nearly to said circumference.
The inner half of the circular body of latch 161 is formed with a projection 1611
that extends into the recessed rim of the hub 124. When the latch is in its normal
position, as in Fig. 41, the outer edge of the projection 1611 allows the
projections 124' of the constantly revolving hub 124 to pass freely by, but whenever
the latch is permitted to rock in its seat the heel of the projection 161¹ is swung
outward into the path of one of said projections 124 and the two hubs 124-129
are immediately locked together and the gear 1291 is caused to revolve. A
spring 162, on the end of hub 129ª, seeks constantly to rock the latch 161 into

page_text: position for such engagement. The clutch section 124 travels constantly in the
direction indicated by the arrow in Fig. 41.
When the escapement lever 149 is rocked on its fulcrum its projecting points 1591
and 159 are swung alternately into the path traversed by the projecting end of
latch 161 and serve as stops to check said latch as well as the hub 129 to which
it is secured. The sudden stopping of the latch also serves to swing its end
outward, against the force of its spring 162, thus throwing the heel of projection 161'
out of locking engagement with the projections 124' of the constantly revolving
hub 124, when hub 129ª and its gear 129¹ stop.
While the feed clutch 121 on shaft 105 is in engagement with the worm gear 117
the cutter carriage 76 moves slowly downward until the bracket 76' engages the
collar 154 and forces the rod 154 downward, when the escapement lever 159 is
rocked from the position shown in Fig. 41 to that of Fig. 42, releasing latch 161
from the point 159º.
Spring 162 then rocks said latch in its circular bearing bringing the heel of
its projection 161' into the path of the revolving points 124¹ one of which
immediately locks with said heel and starts the hub 129 and its gear 129¹.
Simultaneously the gear 130 is revolved and the cam-roll 131 forces plate 133
over into the position in full lines in Fig. 42. This movement of plate 133 rocks
shaft 128, and the segment 129 on its other end slides clutch 121, on shaft 105,
into engagement with the quick return gear 104 and starts the cutter-shaft
carriage 76 upward at a rapid rate.
So soon as the bracket 76' of said carriage reaches the collar 154' the rod 154
is moved upward and the escapement lever is rocked to release the end of latch 161
from the points 1591 of said escapement. The latch is then rocked by its spring
and locks with one of the points 124' and gear 1291 is again started forward but
is immediately checked by the anchor-point 159ª.
This limited movement, instead of rocking plate 133 and shaft 128 sufficiently
to slide clutch 121 back into engagement with the worm-gear 117, serves to bring
said clutch back only half way, to a point where the bolts 120 are out of engage-
ment with their respective notches at both ends of the clutch when, for a time,
the cutter shaft carriage 76 is at rest, and, during this time of rest, the spacing
mechanism is set in motion, as I shall now explain.
Reference to Figs. 7, 8, 9, 32, 44 and 45 will help to explain several discs, pawls,
shields etc., mounted upon the rock-shaft 128. I have referred already to clutch-
discs 127 and 127' on shaft 126, the former (127) being loose on said shaft and
constantly revolving while the latter (127') is fixed on said shaft and only revolves
when clutched to the section 127.
Section 127 is provided with a rock-latch 127 of the same form as the latch 161
described in detail above and the companion section 127 has one or more inward
projections identical in form and action with the projections 124¹ and adapted to
lock with said latch 127. Upon shaft 128, nearly in vertical alignment with
shaft 126, is a disc 163 whose rim is provided with notches 164 of such size and
depth that the projecting end of latch 127b may pass therethrough at such times as
the disc 163 is revolved to bring the spaces or notches 164 into the circular path
of said latch. At other times the solid portions of the disc 163, between said notches,
serve as stops that check the latch 127 and, by rocking the latter in its circular
seat, disengage the two discs 127-127' and thus stop the latter and its shaft 126,
as well as the connected blank-spacing mechanism and cam-shaft 135. The moving
and timing of the notched disc 163, to thus control the spacing mechanism, forms
one of the essential and novel features of my invention. Said notched disc is
loosely mounted on shaft 128 and is formed with an extended hub on which is
fastened, by a set screw 165, a disc 166 which also has a hub on which is mounted
a ratchet disc 167, whose teeth equal in number the notches of disc 163.
Said notched disc and ratchet are here shown as separate pieces, because more
easily adjusted into proper relation if so constructed, but operate as one piece only
and may be so constructed if desirable.

page_text: Next to said ratchet disc is a plate 168 that is secured to shaft 128 and bears a
spring pressed pawl 169 adapted to co-act with said ratchet teeth. When the
pawl-plate 168 is rocked in one direction its pawl 168 partially rotates the ratchet-
dise and also the connected notched-disc 163 to bring one of the notches 164 into
coincidence with the latch 127" to release said latch or, per contra, to move said
disc 163 properly to check said latch.
170 indicates a plate that is loosely mounted on the ratchet-disc 167 and has an
upwardly extending arm to which is attached an operating handle 171 that extends
outward through the wall of bed 50 as best seen in Figs. 4 and 5. Hung in the
lower side of this plate 170 is a spring pressed pawl 172 that also engages the
teeth of the ratchet 167. By grasping handle 171 of this pawl-plate 170, and
slightly rocking the same, the ratchet 167 and the connected notched disc 163 may
be rocked independently of the pawl 169 which latter is intended to be operated
automatically by the rocking of the shaft 128.
Upon the hub of the pawl-plate 168 is a rocker-plate or shield 173
(see Figs. 9, 44 and 45) whose rim is, in the main, circular but is cut away
as at 174, adjacent to the pawl 169. The end of said pawl has a laterally
extending portion 169ª which overlaps the said shield 173. When the shield is in
its normal position, that is to say, while a gear is being cut, the pawl and shield
occupy the relative positions shown in Fig. 44, when the pawl 169 is free to engage
the teeth of the ratchet disc 167, but whenever shield 173 is rocked as shown in
Fig. 45 (which occurs just before the finishing of a gear) the circular edge 175 of
said shield prevents the pawl from engaging with said ratchet.
A portion of the edge of shield 173 is cut with gear teeth 176 that mesh with
teeth 177 on a lever 178 hung on a stud 179.
The upper end of said lever is connected with a spring 180 (see Fig. 9) that
seeks constantly to draw said upper end in the direction indicated by the arrow
in said figure. The upper end of said lever is also connected with a rod 181 that
extends along the front of the machine (see Figs. 1, 4, 18 and 19) and has
adjustably connected therewith, by set screw 182, a crank-arm 183 secured to a
shaft 184. This shaft bears a gear segment 185 that meshes with a rack 186
mounted in the carriage 54 and whose end serves as a bolt that may enter a
notch 187 in a ring 188 clamped upon the enlargement 57 of the hollow spindle 56,
by a set-screw 189 (see Fig. 18).
When a gear-blank has been spaced to receive its last cut, notch 187 is brought
into coincidence with the end of bolt. 186, but said bolt is kept from shooting forward
into the notch by a stud 178ª projecting laterally from the lower arm of the
lever 178, which stud abuts, for the time, a projection 168" on the pawl-plate 168.
Stud 178 is attached to a bolt 178" whose lower end is headed and bears a
spring 178 that seeks constantly to draw the bolt and stud 178ª downward, but
which may yield slightly, as will be understood from the drawings.
In order to attract the attention of the operative to the completion of a gear,
I have provided an alarm that acts when the last tooth of the gear has been cut
and upon the commencement of the final quick return movement of the cutter
carriage.
This aların consists of a bell 207' fixed to the spacing box (see Fig. 1) and rung
by a hammer 208¹ attached to the upper end of lever 178 within the spacing box.
Said hammer is pivoted to the lever 178 as shown in Fig. 46, and projects through
a slot in the spacing box, as seen in Fig. 1. Referring now to Fig. 8, the enlarged
hub 127 of mitre gear 12 bears a small projection 127°.
The rocking of shaft 128 to slide clutch 121 also serves to rock the pawl-
plate 168 backwards when the projection 168ª passes below the end of stud 178ª
and spring 180 immediately rocks lever 178 into the position of Fig. 45 and causes
the bolt 186 to shoot forward into notch 187.
When lever 178 is thus swung into the position of Fig. 45 by the completion of
the cutting of a gear, as described, the shorter end of the hammer 208¹ is moved
into the path of the projection 127 and said hammer is lifted by said projection at

page_text: each revolution of hub 127. As said projection passes out of contact with the
hammer the latter is caused to strike the "bell by means of a spiral spring 209¹
shown in Fig. 46.
The rocking of lever 178 also serves to partially rotate the shield 173, bringing
its projecting portion 175 beneath the end of the pawl 169, thus preventing the
operative engagement of said pawl with the ratchet disc 167. Meanwhile the
cutter-carriage, has been carried to its highest position by the quick return
mechanism, and the bracket 76' engages the collar 154' to rock the escapement
lever 159 and, through its connections, rock the shaft 128 to slide clutch 121 into
its intermediate position, when the cutter carriage stops.
Ordinarily when shaft 128 is thus rocked to bring clutch 121 into its
intermediate position, pawl 169 engages the ratchet disc to rock the notched
disc 163 and so set in operation the spacing shaft 61, but it will be remembered
that the shield 173 has now been rocked to throw said pawl out of engagement
with the ratchet disc and, consequently, the pawl rides idly on the raised
portion 175 of the shield, and the several operations of the machine are
practically at a standstill. The operator then swings lever 178 into the position
of Fig. 44 thus moving the bell hammer out of the path of the projection 127°
thus stopping the alarm.
After a new blank has been substituted for the cut one the handle 171 of
the pawl plate 170 is grasped and rocked to the left hand (as viewed from the
front side of the machine) thus causing its pawl 172 to partially rock the
shaft 128 and bring one of the spaces 164 coincident with latch 127b.
This movement of the disc 163 releases the latch 127 which, by reason of its
spring, is rocked in its circular seat and at once locks with the constantly revolving
clutch section 127 and begins to rotate with the latter, thus starting the shaft 126
which through the gearing 149-151 and 153, starts the spacing shaft 61 and
partially rotates the blank-support to take up all back-lash and bring the blank
into position to cut its first tooth.
So soon as the shaft 126 is thus started, motion is also imparted through the
gears 138-139 to the cam shaft 135 and as said shaft revolves, the cam 134 engages
roll 136 and rocks shaft 128 and plate 133 into the position shown in Fig. 41. Two
important results are attained by thus rocking shaft 128; first, the notched disc 163
is rocked with said shaft and brings one of the teeth or partitions (between the
notches 164) into the path of the latch 127 resulting in stopping said latch and
throwing it out of locking engagement with the constantly revolving section 127,
when shaft 126, and the connected blank-spacing mechanism, as well as the cam-
shaft 135, stop and second, the rocking of shaft 128 by cam 134 also serves,
through the segment 129, to slide the clutch 121 into lock with the worm-gear 117
and thus start the slow feed movement of the cutter carriage.
It will thus be seen that, upon the completion of each important step or operation,
certain mechanism controlling the next succeeding important step, is released and
started into action and that if, for any reason whatsoever, any one of the important
mechanisins fail to act all succeeding operations will be held in check and will not
be allowed to operate.
It will be seen also that the various mechanisms are all driven positively by
means which consume power only while in action, thus preventing any drag upon
the machine, and all undue wear of the parts.
While my described. gear cutting machine is particularly designed to work
automatically, provision is made so that the cutter carriage may be fed by
hand if desired, thus making my machine more valuable for general machine
shops use.
By referring to Figs. 26, 27, 28 and 40, it will be seen that I have provided on
shaft 105 a splined clutch section 190 that may co-act with a companion clutch
section 191 on the end of the hub of the loosely mounted mitre gear 106.
Section 190 is formed with an annular groove in which lies the fork end of an
arm 193 which is movable in a direction parallel with shaft 105. The other end

page_text: of said arm 193 is connected by a crank 194 with a rock-shaft 195 extending
toward and through the front wall of the machine bed and having secured to it,
ontside said bed, an operating handle 196 by means of which the shaft 195 may be
rocked to throw the clutch section 190 into or out of engagement with the
companion section 191, as will be understood by the drawings.
"
When the said clutch sections are disengaged, as in Fig. 40, the automatic feed
mechanisms for the cutter-carriage, both slow and "quick return," become
inoperative and in order to move said cutter carriage I extend the hinge pintle or
shaft 72 (see Fig. 4) so that an ordinary crank, or hand wheel, may be fixed on
said extension with which to rotate said pintle by hand and thus feed the cutter
carriage upward or downward, as may be desired.
"
.
My machine is also adapted for "hobbing worm gears and this without
requiring any changes in the described construction. When the machine is to be
so utilized a hobbing cutter, identical in pitch and size with the worm or screw,
which is to be used with the worm-gear, is secured on the cutter shaft 83. The
worm-gear blank is then mounted on a mandrel that is held in spindle 56. The
automatic feed mechanism for moving the cutter-carriage is then thrown out of use
by disengaging the clutch 190-191, leaving the hobbing cutter free to revolve
continuously in a single horizontal plane. It now becomes necessary to start the
shaft 61, which serves as the spacing shaft for ordinary gears and to cause said
shaft to revolve continuously instead of intermittently.
Having thrown out of service for the time, the catter carriage feeding mechanisms
and the devices which form the connecting link between said mechanisms and the
shaft 126, it is only necessary to rock the lever 170 and through its pawl 172, rock
the disc 163 until one of the notches of the latter is made to register with the
latch 127. Said latch, being thus released, immediately locks with the clutch
section 127 and shaft 126 begins to revolve. Through the train of gearing 149-
151 153 the shaft 61 is simultaneously started and inasmuch as the devices that
ordinarily control the notched disc 163 are thrown out of service the latch 127b
will continue to revolve, passing without hindrance through the coincident notch of
said disc 163.
Thus the hobbing cutter and the worm-gear blank are revolved continuously,
the cutter gradually cutting its way into the blank.
In order to thus utilize my machine for "hobbing" it is, of course, necessary
that the blank and cutter shall be driven at the same relative speeds that the
finished gear and its coacting worm will have when put to use and this I am able
to accomplish by suitably changing one or all of the gears 149-151 and 153.
In order to produce this result conveniently I prefer to so organize the machine
that the speed of the constantly revolving element 127 coincides with that of the
cutter shaft, which result I accomplish by making the ratio of the gearing
connecting this element (127) and the driving shaft 84 equal to that connecting
said shaft 84 and the cutter shaft.
"
Fig. 5 illustrates a bolt 197 that is fitted to slide vertically in the "spacing
box and is forced upward by a spring 198, as clearly shown. The exposed end
of said bolt is provided with a knob or head 199 and its upper end engages the
end wall of a spiral cam groove 127d cut on the clutch section 127¹. When the
clutch section 1271 is set in motion, the said cam gradually forces bolt 197 outward
until a complete revolution of the cam has been made, when the bolt snaps from
the highest to the lowest point of the cam and then serves as a lock to prevent
backward rotation of the clutch section 127'. The end of latch 127b, resting
against the notched disc 163, serves at the same time to prevent said section from
revolving in the opposite direction.
By thus locking the section 127¹ against rotary movement in either direction all
tendency to work loose or become displaced is forestalled and prevented. It should
be noted that the bolt end 197 is bevelled at one side in such manner that if the
clutch section 1271 should fail to make a complete revolution or, if the shock
resulting from the sudden impact of latch 127" against the notched disc should

page_text: cause section 127' to recoil slightly, the point of bolt 197 will enter and be forcel
home by spring 198. When my machine is to be used for "hobbing," as above
explained, it is desirable that bolt 197 be withdrawn so that it may not act as a
drag on the then constantly revolving clutch section 127', so I have slotted the
said bolt longitudinally as at 200 and have cut a short lateral notch at the upper
end of said slot.
Through the slot thus provided I have passed a pin 201 that is seated in the
wall of the spacing box. When it is desired to withdraw bolt 197 from operative
engagement with the cam 127d it may be quickly and effectually done by drawing
the bolt downward and turning it a partial revolution, causing the said lateral
notch to pass over the pin 201.
When my machine is to be used for "hobbing" worm-gears the gear 98 should
bear the same ratio to gear 99 as the bevel gear 91 does to gear 92.
Figs. 37, 38, 39 and 40 illustrate a graduated coupling, which connects shaft 126
with gear 149 or, more properly with the collar on which said gear is mounted.
Fig. 38 explains most clearly the construction and arrangement of the various
parts of said coupling. Keyed upon shaft 126 is a disc 202 whose face is cupped
to receive a circular plate 203 whose entire periphery is finely serratei as at 204
and whose exposed face is graduated to correspond to said serration.
Said plate
is here shown as formed with 360 serratious but the number is not material.
Dovetailed in the outer edge of disc 202 is a plate 205 arranged to interlock with
a screw 206 that is tapped into the edge of said disc 202 as clearly seen in Fig. 38.
The inner end of plate 205 is curved and serrated to conform to the serrated
periphery of the graduated plate 203. By partially unscrewing the screw 206 the
plate 205 may be moved in its ways to release its serrations from those of the
plate 203, when the latter named plate may be revolved within disc 202. The
projecting portion of shaft 126 is reduced in diameter and has mounted thereon a
collar 207 provided with an annular flange 208 over which is fitted a rebated
ring 209 that is secured to the graduated plate 203 by screws 210 and serves to
clamp the flanged collar 207 firmly to the graduated plate.
Collar 207 is turned down, as at 211, and splined to receive the initial gear 149
of the train that transmits motion from shaft 126 to the spacing shaft 61.
It is frequently found desirable, in fact necessary, to adjust the spacing shaft 61.
without disturbing its driving shaft 126 as, for example, in making two or more
cuts through a single tooth to provide greater clear space or in cutting bevel gears
which, to be correct, should have both the teeth and intervening spaces converging
to the apex of the pitch cone and this can be accomplished only by "setting
over" the blank slightly after a single cut has been made and making a second
cut which, instead of being parallel with the first cut, will lead toward said apex
and thus produce teeth and spaces that are gradually narrower as they approach
said apex.
The described graduated coupling makes it both possible and easy to
thus adjust shaft 61 independently of the shaft 126, it being only necessary to
unscrew the screw 206 and withdraw the serrated plate 205 from the edge of the
graduated plate 203 when said plate as well as the collar 211, the train of
gearing 149, 151, 153, and shaft 61 may be rotated without disturbing shaft 126
and its disc 202. By utilizing the graduated plate 203 a succession of fine
adjustments may be accurately made if desired. After such adjustment has been
made the screw 206 is screwed home to force the sliding plate 205 into locking
engagement with the serrated edge of plate 203. The coupling thus provided is
then as strong and effectual, for the purpose in hand, as if the gear 149 was
secured immediately to the shaft 126.
Should it be desired to disconnect the described coupling, so that the shaft 61
may be freely revolved, the screws 210 may be unscrewed, when the flanged
disc 207, to which the gear 149 is secured, may revolve freely in the ring 209. It
will thus be understood that either a very fine adjustment of the coupling sections
may be attained (by means of screw 206 and plate 205) or that said coupling
sections may be entirely disengaged by releasing screws 210.

page_text: I have referred briefly to the notched ring 188 that is located on the blank-
supporting spindle 56 and whose notch may coact with bolt 186 under certain
conditions.
This ring is adjustable in its seat and is intended to register with the bolt 186
when the blank has been spaced for the last tooth. For greater convenience and
accuracy in setting the ring 188 I have graduated its circumferential edge as
at 185 and have provided a zero mark on the carriage 54 over the bolt 186.
In cutting ordinary gears it is only necessary to start with the bolt 186 coincident
with the notch of ring 188. When however it is desired to cut gear-segments the
ring 188 should be so set that the notch will be brought into coincidence with the
bolt when the last tooth of the required segment shall have been spaced off.
Referring to the described mechanism for rocking shaft 128, shown and described
as gear 130, eccentric roll 131 and rock shaft arm 133, I wish it understood that
while this is my preferred form, owing to its adaptation to the shape and location
of the parts, yet any equivalent rocking device set in motion by means of the
described intermittent clutch, is within my invention.
Referring also to the described construction of intermittent clutches mounted
on shafts 99 and 126, I wish to state that any equivalent positively driving
intermittent clutch suited to the requirements as set forth in the foregoing
Specification, falls within my invention as applied to automatic gear cutting
machines; the construction shown being my preferred form of such clutch.
I wish also to define my use of the terms intermittently," "intermissions," etc.,
in describing and claiming the movements of the cutter-carriage of my improved
machine, as referring to intentionally designed and prolonged periods of rest,
during which other movements of various parts of the machine occur, as herein
described, in contra-distinction to the momentary periods of rest common to the
cutter-carriages of other gear cutting machines at the point of reversal, which are
incidental only, and due to the disengagement of the feeding clutch while passing
the neutral point between the clutch drivers. In the machines of this class,
already well known, the cutter-carriages may properly be said to reciprocate
rather than to move intermittently.
Having now particularly described and ascertained the nature of my said
invention and in what manner the same is to be performed, I declare that what
I claim is -
1. In a gear cutting machine, the combination of a blank-holder, automatic
mechanism for revolving said holder intermittently, a cutter carriage mounted to
slide as set forth, and automatic mechanism for moving said cutter carriage
intermittently, all substantially as specified.
2. In a gear cutting machine, the combination with a suitable frame, of a
sliding cutter carriage, automatic mechanism for sliding said carriage inter-
mittently, a revoluble blank-holder and mechanism for revolving said blank-holder
during the intermissions in the movement of said cutter-carriage.
3. In a gear cutting machine, the combination with a suitable frame, of a
sliding cutter carriage, automatic mechanism for sliding said carriage inter-
mittently, a revoluble blank-holder, and positively driving mechanism for revolving
said blauk-holder during the intermissions in the movement of said cutter carriage.
4. In combination, a blank holder, mechanism for revolving the same
intermittently, a cutter carriage mounted to slide as set forth, and positively
acting mechanism, driving the said blank revolving mechanism and cutter carriage,
and timed to start the latter only upon the completion of the intermittent
movements of the blank holder, all substantially as specified.
5. In combination with a revoluble blank holder, mounted to travel on ways,
mechanism for revolving said holder intermittently, a cutter carriage, mounted to
travel in a direction parallel with the axis of the gear blank, and hinged to swing
at an angle to said axis, mechanism for moving said cutter carriage intermittently,
positive clutch mechanism for actuating said cutter carriage and driving mechanisın,

page_text: and means for automatically stopping the cutter carriage while the blank holder is
being revolved, all substantially as specified.
6. In an automatic gear cutting machine, wherein the various movements are
actuated by a single driving shaft, the combination of a blank holder, means for
revolving said holder intermittently, positive clutch mechanism for controlling such
revolution of the blank holder, means for starting said clutch mechanism into
action, a cutter shaft and mechanism intermediate said 'driving shaft and cutter
shaft for revolving the latter.
7. In combination with a revoluble blank holder, mounted to travel on ways,
mechanism for revolving said holder intermittently, a cutter carriage mounted to
travel in a directión parallel with the axis of the gear blank, and also inclinable at
an angle to said axis, a cutter-shaft journalled in said carriage, a fixed driving
shaft and mechanism substantially as set forth, intermediate said driving shaft and
cutter shaft for revolving the latter.
8. In a gear cutting machine, the combination with a suitable framework having
a revoluble blank holder and a sliding cutter-spindle-carriage thereon, of a driving
shaft mounted in fixed journal bearings upon said frame, splined shaft (90) pivotally
attached to said cutter spindle and said driving shaft, gears (88) (89) connecting
said driving shaft and said splined shaft, and gears (91) (92) connecting said
splined shaft and said cutter spindle, substantially as described.
9. In a gear cutting machine, the combination with a suitable frame or bed,
having revoluble blank holder and a sliding cutter spindle carriage thereon, of a
driving shaft mounted in fixed journal bearings upon said frame, splined shaft (90)
pivotally attached to said cutter spindle and said driving shaft, gears 88-89
connecting said driving shaft and said splined shaft, and gears 91-92 connecting
said splined shaft and said cutter spindle, and the arm 94 adapted to support the
journal bearings of said splined shaft to keep them in alignment, substantially as
described.
,
10. In combination, a cutter shaft journalled in a carriage, mounted to slide on
ways, and also hinged to be swung at an angle with said ways, gear 92 fixed on
said shaft, driving shaft 84 having secured thereon a bevel gear 89, and shaft 90,
having fixed on one end a bevel gear 91 meshing with said cutter-shaft gear 92,
and having splined on its other end a bevel gear 88; the shaft 90 being journalled,.
adjacent to its gear 91, in a stand secured to an arm 94 that is swivelled on the
cutter shaft at one end, and arranged to straddle and slide on the driving shaft 8+,.
all substantially as and for the purpose specified.
11. In a gear cutting machine in combination with a blank holder, adjustably
mounted on ways, and means for revolving said holder intermittently, and a cutter
shaft journalled in a carriage, mounted to slide in a direction parallel with the axis
of the blank, and hinged to be adjusted at an angle to said axis as set forth,
mechanism substantially as specified for revolving said cutter-shaft continuously,
and also for feeding the cutter shaft carriage intermittently, for the purpose
specified.
12. In a gear cutting machine the combination with a suitable frame, of a
revoluble blank holder, an inclinable cutter carriage support, a cutter carriage
mounted to slide thereon, a feeding shaft forming the pivot of said carriage
support, a feeding screw mounted in said carriage support, and gears connecting
said pivot shaft and feeding screw, substantially as described.
13. In a gear cutting machine, the combination with a suitable frame having
mounted thereon a revoluble blank holder, and a sliding cutter carriage, of an
initial reversible feeding shaft mounted in fixed journal bearings on said frame, a
feeding screw for said cutter carriage and gearing connecting said initial reversible
feeding shaft and feeding screw, substantially as described.
14. In a gear cutting machine, the combination with a suitable frame, having
mounted thereon a revoluble blank holder, an inclinable cutter-carriage-support
with a cutter carriage mounted to slide thereon, a feeding screw mounted in said
cutter carriage support, and gears connecting said feeding screw with a shaft

page_text: forming the pivot of said inclinable cutter-carriage-support, of an initial reversible
feeding shaft mounted in fixed journal bearings, and gearing connecting said initial
reversible feeding shaft with the pivotal shaft of said inclinable cutter carriage
support, substantially as described.
15. In a gear cutting machine, the combination of a blank holder, means for
revolving the said holder intermittently, a cutter carriage and shaft mounted to
travel on ways, means for removing said cutter carriage consisting of a shaft with
oppositely moving clutch drivers thereon, and a sliding clutch upon said feed shaft,
and automatic mechanism for moving said clutch from one of said drivers, to the
companion driver, and for returning said clutch by two movements, the first of
which stops the clutch midway said drivers and provides a period of rest for the
cutter feeding mechanism, all substantially as specified.
16. In combination with a blank holder, and mechanism for revolving the same
intermittently, a cutter-shaft-carriage mounted to slide in a direction parallel with
the axis of the gear blank, mechanism for moving said cutter shaft carriage,
consisting of a shaft with oppositely moving clutch drivers thereon, a sliding clutch
upon the said feed shaft, a rack 123 attached to said clutch, a gear segment 129 in
mesh with said rack, and means substantially as specified for rocking said
segment.
17. In combination with a blank holder, mounted adjustably on ways, mechanism
for revolving said holder intermittently, a sliding cutter-shaft-carriage, means
substantially as described for moving said cutter shaft carriage intermittently and
clutch mechanism as 190, 191 forming an element of said cutter-carriage moving
mechanism whereby the latter may be disconnected, all substantially as specified.
18. In combination with a blank holder, and mechanism for revolving the same
intermittently, a cutter-shaft-carriage mounted to slide in a direction parallel with
the axis of the gear blank, a rod 154, mounted to slide at one side of said carriage
and provided with adjustable collars 154', 154, a bracket 76' secured to the cutter
carriage, adapted to engage said collars to slide shaft 154, mechanism for moving
said cutter-shaft-carriage intermittently, and mechanism connecting the rod 154
and the cutter carriage actuating mechanism, substantially as described.
19. In a gear-cutting machine, clutch-sliding mechanism, consisting of a constantly
revolving shaft 99ª, an intermittent clutch as 124-129ª, intermittently acting
mechanism as eccentric 130, rock shaft arm 133 having the relatively wide
opening 132, rock-shaft 128, and mechanism substantially as set forth connecting
said rock shaft and said sliding clutch so organized that said eccentric will cause
said clutch to slide further in one direction than in the opposite direction, in
combination with a cam 134 connected with the blank revolving mechanism and
adapted to continue the shorter movement of said sliding clutch before said blank
revolving mechanism stops, substantially as described.
20. In a gear cutting machine, the combination of a sliding cutter carriage,
having a stop bracket 761 secured thereto, a stop rod 154 mounted to slide in a
direction parallel with said cutter carriage, and provided with adjustable stop
collars 154-154", a lever 159 connected to rod 154, rock-shaft arm 133 having
projections 133-133ª, rock shaft 128, sliding clutch 121, and mechanism
connecting said clutch and said rock shaft 128 so organized that contact of said
stop bracket 76¹ with said stop collars will move said clutch 121, substantially as
and for the purpose specified.
21. In a gear cutting machine, the combination of a sliding cutter carriage
having a stop bracket 76' secured thereto, a stop rod 154 mounted to slide in a
direction parallel to said cutter carriage and provided with adjustable stop collars
as set forth, a constantly revolving shaft 99ª provided with an intermittent clutch
substantially as described and an escapement lever 159 co-acting with said clutch,
all so organized that contact of said stop bracket 76' with said stop collars will
release said intermittent clutch, substantially as described.
22. Blank revolving mechanism consisting of a constantly revolving element
as 127, a shaft 126 upon which said element 127 is loosely mounted, a

page_text: revoluble black holder, mechanism as set forth connecting said shaft 126 and
blank holder and positively engaging clutch mechanism for locking together the
said element 127 and the shaft 126.
23. In a gear cutting machine, blank revolving mechanism consisting of a
constantly revolving driving element as 127, a positively driven intermittently
revolving shaft 126, a revoluble blank holder and mechanism connecting said shaft
and said blank-holder, in combination with mechanism for controlling the
engagement of said driving element 127 and the intermittently revolving shaft 126,
all substantially as described.
24. In a gear cutting machine, a blank revolving mechanism consisting of a
constantly revolving driving element 127, a positively driven intermittently
revolving shaft 126, clutch bub 127¹ mounted on said shaft and provided with a
latch 127, rock shaft 128, having mounted thereon pawl plate 168, provided with
pawl 169, and notched disc 163 provided with ratchet 167; all combined and
operating substantially as described.
25. In a gear cutting machine, blank revolving mechanism consisting of a
constantly revolving driving element 127, a positively driven intermittently
revolving shaft 126, clutch-hub 1271 mounted on said shaft and provided with a
latch 127, rock-shaft 128 having mounted thereon pawl-plate 168, with its
pawl 169, and notched disc 163 provided with ratchet 167, and mechanism for
rocking shaft 128 to cause the pawl to move the notched disc; all being combined
substantially as specified.
26. In a gear cutting machine, blank revolving mechanism consisting of a
constantly revolving driving element as 127, a positively driven intermittently
revolving shaft 126, clutch hub 1271, mounted on said shaft and provided with
latch 127, notched disc 163 mounted on shaft 128 and provided with ratchet 167,
and a hand lever 170 with its pawl 172 mounted to coact with said ratchet and
notched disc; all combined and operating substantially as described.
27. In a gear cutting machine, blank revolving mechanism consisting of a
constantly revolving driving element as 127, a positively driven intermittently
revolving shaft 126, means for connecting said shaft and said driver, and gears 138
mounted on shaft 126, in combination with shaft 135 provided with gears 139, and
mechanism substantially as described for controlling the connection between
shaft 126 and its driver.
28. In an automatic gear cutter wherein the various movements are actuated by
a single driving shaft, the combination of a blank holder and means for revolving
the same intermittently, a cutter carriage mounted to travel in a direction parallel
with the axis of the gear blank, mechanism for moving said cutter carriage
intermittently, and means consisting of gears 138, 139, in the train of mechanism,
whereby the initial revolutions of the blank revolving mechanism may be varied
for the purpose specified.
29. In an automatic gear cutting machine, the combination of a blank holder,
and means for revolving the same intermittently, a cutter carriage mounted to
travel in a direction parallel with the axis of the gear blank, mechanism for moving
said cutter carriage intermittently, means consisting of gears 138-139 in the train
of mechanism whereby the initial revolutions of the blank revolving mechanism
may be varied, and an indicator or tell-tale consisting of spring pressed pins 148
adapted to engage with said gears 139, substantially as described.
30. Blank revolving mechanism consisting of a constantly revolving driving
element as 127, a positively driven intermittently revolving shaft 126, provided
with an index coupling substantially as set forth, a revoluble blank holder and
mechanism connecting said coupling and blank holder, all combined substantially
as described.
31. Blank revolving mechanism consisting of a constantly revolving driving
element as 127, a positively driven intermittently revolving shaft 126, provided
with a clamp coupling consisting of a driving element 202 mounted upon said
shaft 126, a driven element 207, means as ring 209 for clamping said elements, a
C

page_text: revoluble blank holder and mechanism connecting said driven element and blank
holder, all combined substantially as described.
32. Blank revolving mechanism consisting of a constantly revolving driving
element as 127, a positively driven intermittently revolving shaft 126, hub 127',
mounted on said shaft provided with latch 1275 and spiral cam seat 127, in
combination with a suitable stop, as notched disc 163, for said latch, and a spring-
pressed bolt 197 adapted to securely lock said shaft 126 when not in revolution,
substantially as described.
33. In a gear cutting machine in combination a blank holder, and mechanism.for
revolving the same intermittently, a graduated notched collar concentric with and
adjustably secured to said blank holder, and a spring actuated bolt seated in the
blank holder support, and adapted to engage said notch, upon the completion of a
predetermined series of movements of said intermittent blank holder, in the manner
and for the purpose specified.
34. In a gear cutting machine, in combination, a blank-holder and mechanism
for revolving the same intermittently, a notched collar adjustably secured to said
blank-holder, a spring actuated bolt seated in the blank-holder support and an
alarm consisting of a bell and hammer and operating mechanism substantially as
herein described, whereby said bell is rung upon the entrance of said bolt into said
notch.
35. In a gear cutting machine, in combination a blank-holder and mechanism for
revolving the same intermittently, a notched collar adjustably secured to said
blank holder, a spring actuated bolt seated in the blank holder support, a spring
actuated lever 178 provided with sliding bolt 178 having projection 178ª, in
combination with rock shaft 128, and a pawl-plate 168 having projection 168",
mounted on said shaft, so organized that said projection 178 on bolt 178b and
projection 168 of pawl-plate 168, will prevent movement of lever 178 until the
suitable rocking of shaft 128, substantially as described.
36. In an automatic gear cutting machine, in combination, a blank holder and
mechanism for revolving the same intermittently, a notched collar adjustably
secured to said blank holder, a spring actuated bolt seated in the blank holder
support, mechanism connecting said bolt with a spring actuated lever 178 provided
with gear segment 177, a coacting toothed ratchet guard 173, with high portion 175,
mounted on shaft 128, a pawl and pawl-plate mounted on said shaft, so organized
as to render the pawl inoperative whenever said lever 178 is suitably moved;
substantially as herein described.
37. In a gear cutting machine, in combination, a driving shaft 84, a cutter
shaft 83, a revoluble blank holder, blank revolving mechanism consisting of a
constantly revolving element as 127 and shaft 126 upon which said element 127 is
loosely mounted, clutch mechanism for locking together said element 127 and
shaft 126, gearing connecting said driving shaft and said element 127 of such ratio
that the element 127 will revolve at the same speed as said cutter shaft, and
gearing connecting said shaft 126 and said blank holder.
Dated this Seventh day of January 1895.
WALLACE FAIRWEATHER,
Chartered Patent Agent,
62, St. Vincent Street, Glasgow, Agent for the Applicant.