Improvements in Machines for Making Gear-teeth.
Year: 1896

page_text: Date of Application, 28th Apr., 1896-Accepted, 5th Sept., 1896
COMPLETE SPECIFICATION.
Improvements in Machines for Making Gear-teeth.
I, HERBERT CURTIS WARREN, of No. 283 Collins Street, in the City of
Hartford, County of Hartford and State of Connecticut, United States of
America, Contractor, do hereby declare the nature of this invention and in what
manner the same is to be performed, to be particularly described and ascertained
in and by the following statement :-
This invention relates to gear-tooth-generating machines; the object of this
invention being to furnish a machine of this class, of improved and simplified
construction and organization, especially adapted for generating the teeth of spur-
wheels with rapidity, precision and economy; and also to provide, in connection
with the machine, a rotative and longitudinally-reciprocative multiplex-cutter of a
length not less than the peripheral length of the gear-blank in which the teeth are
to be cut, and to so construct and organize the multiplex-cutter and associated
mechanism that a portion of the entire circuit of teeth will be cut in the gear-blank
at each working-stroke of the cutter.
Referring to the sheets of drawings, hereunto annexed, corresponding characters
indicate like parts in all the figures.
Figure 1 is a plan view of the gear-tooth-generating machine, parts being broken
away, and the cutter being shown in its retracted or starting position.
Figure 2 is a side view of the machine, as seen from the right hand in Fig. 4.
Figure 3 is a side view of the machine, as seen from the left hand in Fig. 4.
Figure 4 is an end view of the machine, as seen from the left hand in Fig. 1.
Figure 5 is a vertical section of the machine, taken in dotted line a-a, Fig. 2,
looking toward the right hand in said figure.
Figure 6 is a sectional plan view of a portion of one end of the machine,
illustrating the organization of the reversing-driving mechanism and subsidiary
elements.
Figure 7 is a side view of the mechanism shown in Fig. 6, as seen from below in
said figure.
Figure 8 is an end of a portion of the mechanism that actuates the belt-shippers,
as seen from the right hand in Fig. 7.
Figure 9 is a sectional end view of a portion of the machine, showing a slightly-
modified form of actuating mechanism between the gear-blank carrier and cutter-
carrier.
The term "multiplex-cutter," as herein used, applies to a rotative rack-like
cutter of cylindrical or polygonal cross-section, comprising a multiplicity of cutters,
each of a cross-sectional shape, in the plane of its axis of rotation, similar to a
truncated wedge; the adjacent cutting-faces of the cutters being separated from
each other by a distance substantially equal to the width of the tooth it is desired
to generate. This tooth-cutter may, in practice, consist of a toothed ring, disk, or
flange, of a shape suitable for generating the required form of gear-tooth.
To generate the teeth of spur-gears, in accordance with this invention, it is
desirable that the gear-blank shall have a continuous rotative movement for a
distance not less than the peripheral length of said blank; and that a multiplex-
cutter such as hereinafter described-be moved into contact with the periphery
of, and along with, the gear-blank in the same direction, uninterruptedly, for a
distance not less than the peripheral length of the gear-blank and with the same.

page_text: peripheral velocity, to thereby generate a portion of each tooth of the entire circuit
of teeth at one cutting operation; and it is further desirable that the direction of
movement of the gear-blank and multiplex-cutter be reversed at every complete
stroke of the cutter; and that said cutter shall be effective for cutting in both
directions of its movement, which may be accomplished by changing the transverse
relation of the gear-blank and cutter at predetermined points in the working
stroke of the cutter.
A theoretical adaptation of mechanism for supporting the gear-blank and
multiplex-cutter in proper co-operative relation, and for automatically effecting
the requisite movements of the gear-blank and cutter to form theoretically-correct
gear-teeth in the gear-blank by progressive, backward-and-forward cutting
operations, is shown in the drawings; but it is desired to state that modified
adaptations of mechanisms may be made without departure from this invention.
As shown in the drawings, the gear-tooth-generating machine comprises, in part,
a continuously-rotative gear-blank carrier C, which is supported for movement
transversely of the axis of the rotative cutter, and which is also supported for
adjustment in a direction transversely of its own axis; a cutter-carrier C,
supported for reciprocation in a plane parallel to a line tangent to the periphery
of the gear-blank G, carried by the gear-blauk carrier; a multiplex-cutter C,
supported for rotation upon its axis substantially at right angles to the axis of the
gear-blank carrier, and comprising a series of peripherally-concentric tooth-cutters
separated in the plane of their axes by intervening tooth-formative spaces; and
actuating mechanism embodying means for continuously rotating the multiplex-
cutter, also for simultaneously imparting a rotative movement to the gear-blank
and a longitudinal movement to the cutter in coinciding directions and at
corresponding peripheral velocities; and also embodying means for simultaneously
reversing the direction of movements of the gear-blank and cutter, and for
intermittently changing the transverse relation of the gear-blank and cutter, as
will be hereinafter more fully described.
The framework of the machine-which may be of any suitable construction for
carrying the operative parts-is shown in the drawings consisting of a main-frame F,
for supporting the cutter-carrier and certain subsidiary elements; and an overhanging
auxiliary-frame F', which is supported for vertical adjustment on the inain-frame F,
and supports the gear-blank carrier and certain elements of its subsidiary mechanism.
The main or cutter-carrier frame F-which is shown similar to an ordinary
planer-frame-consists of the base B, having the usual longitudinal guideways 2,
and having uprights B1 and B2, located at opposite sides and near the middle
portion of the bed; which uprights B and B have vertical slideways 3 and 4,
respectively thereon, to receive the slides 5 and 6 on the auxiliary or gear-blank-
carrier frame F¹.
The slides 5 and 6 on the frame F¹ are carried for vertical adjustment on the
slideways 3 and 4, respectively, of the uprights B' and B', and are shown in the
nature of brackets having horizontal bearings 7 and 8, respectively therein, which
are axially coincident and. are transversely disposed relatively to the plane of
movement of the cutter C, as shown most clearly in Fig. 5 of the drawings, and
support the gear-blank carrier C.
For adjusting the blank-carrier frame F¹ vertically of the cutter-carrier frame F,
suitable blank-carrier-adjusting mechanism is provided, which may consist of two
adjusting-screws 9 and 10, journaled in bearings at 12 and 13 at the upper end and
at opposite sides of the frame F, and having screw-threaded bearings at their lower
ends in the upper ends of the uprights B1 and B2, respectively; said adjusting-
screws 9 and 10, being shown provided at their upper ends with bevel-gears 9
and 10', which mesh with bevel-gears 14 and 15, respectively, at opposite ends of
a shaft 16, journaled in horizontal bearings 17 and 18 at opposite sides of the
frame F. This shaft has an angular end 16', to which a crank or wrench may be
applied for rotating the same, which will raise or lower the blank-carrier frame F',
as will be understood by reference to Figs. 1 and 5.

page_text: The cutter-carrier C, which is shown supported for reciprocatory move nents on
the guideway 2, has bearings 19 and 19 at opposite ends thereof, to receive the
ends of the shaft or core of the multiplex-cutter C2; which cutter C² may comprise
a multiplicity of tooth-milling cutters 21, detachably fixed to the shaft 20, and
having tooth-formative spaces intermediate thereto.
It is desired to state, in the above connection, that, while it is preferable to
employ a multiplicity of independent milling-cutters, and fix them to a shaft, as
shown in the drawings, this construction and arrangement might be modified
somewhat, without departure from the invention.
For convenience, the shaft 20 and the milling-cutters 21 thereon will, as a whole,
be hereinafter termed the "multiplex-cutter"; said multiplex-cutter being somewhat
in the nature of a rotative, cylindrical rack, the teeth of which have cutting-faces
of a shape corresponding to the shape of the tooth-space to be cut in the gear-blank.
In practice, the multiplex-cutter C will have its cutting-faces and intervening
spaces of an aggregate length, longitudinally of the axis thereof, uot less than the
peripheral length of the gear-blank to be operated upon; and it will be adapted
for generating a portion of each tooth of the entire circuit of teeth at every
complete stroke of the cutter.
As a means for continuously rotating the cutter C, simultaneously with the
reciprocatory movements of said cutter, the shaft 20 of the cutter is shown in
Figs. 1 to 4, inclusive, furnished with a spur-wheel 22 in gear with a pinion 24
through the medium of an intermediate idle-wheel 23; and this pinion 24 has
a hub 241, journaled in a bearing 25 upon a bracket 26 of the cutter-carrier C', and
is held in place, so as to move with the carrier and bracket, by means of an
internally screw-threaded collar 27, screwed on the end of said hub 24', as shown
most clearly in Fig. 2 of the drawings. The pinion 24 is splined to move
longitudinally of a cutter-rotating driven-shaft 28, which is supported at opposite
ends in bearings 29 and 291 upon the side of the cutter-carrier frame F; said
shaft 28, being driven continuously in one direction through the medium of a
suitable driving mechanisın, (designated in a general way by D,) and in a manner
hereinafter more fully described.
As a means for reciprocating the cutter-carrier, said carrier is shewn provided on
its under side with a longitudinally-disposed rack 30 in mesh with a driving-
pinion 31 on a driven-shaft journaled in transverse bearings 32 and 321 on the
cutter-carrier frame F; which shaft is furnished at its outer end with a worm-
wheel 33, which is driven by a worm 34 upon a driving-shaft 35, journaled in
bearings on the side of said frame; and which shaft 35 is rotated, first in one
direction and then in an opposite direction, to advance and retract, respectively, the
cutter-carrier by means of the driving mechanism D, which is in the nature of a
reversing-driving mechanism, and which also actuates the cutter-rotating shatt 28.
The gear-blank carrier C comprises two longitudinally-separable members 36
and 37, which are connected together for movement in the same plane, longitudinally
of their axes and transversely of the multiplex-cutter C. These members 36 and 37
are shown conically recessed at 38 and 38', respectively, at their inner adjacent
ends, to receive the conical ends 39 of the gear-blank-supporting arbor 40; which
arbor supports the gear-blank G and constitutes a connector between the two
carrier-members 36 and 37, and is held in place by means of clamp-rods 41 and 42,
which extend through axial bores in the two members 36 and 37, respectively.
These rods are in the nature of bolts having screw-threaded bearings at their inuer
ends in the opposite ends, respectively, of the arbor 40, and having heads 41' and 421
in bearing engagement with the outer ends of the carrier-members 36 and 37,
respectively, as will be understood by reference to Fig. 5 of the drawings.
One of the carrier-members, as 36, is shown journaled for rotation in a rack-like
sleeve 43, supported for reciprocatory movement in a horizontal bearing, as 7, at
the lower end of the blank-carrier frame F; whereas, the other carrier-member,
as 37, is shown splined for longitudinal movement in a rotative sleeve 44, journaled
in a horizontal bearing, as 8, located at the lower end of the blank-carrier frame F¹

page_text: in axial alignment with the bearing 7, before referred to. This last-mentioned
sleeve 44 is held against reciprocatory movement in the bearing by suitable flauges
at the ends thereof, as shown in Fig. 5.
For the purpose of effecting a rotative movement of the gear-blank carrier C in
synchronism with the reciprocatory movement of the multiplex-cutter, said carrier C
will be controlled in its movements by the cutter-carrier C¹, and will be actuated
from said cutter-carrier through the medium of synchronizing actuating mechanism,
(designated in a general way by S,) operatively connecting the gear-blank carrier
and cutter-carrier.
This synchronizing actuating mechanism S, which constitutes an actuating-
connector between the gear-blank carrier C and cutter-carrier C¹, may, in the
simplified form thereof shown in Fig. 9 of the drawings, consist of a rack 45, fixed
to the upper face, and extending longitudinally of the cutter-carrier at one side the
axis thereof, and a spur-wheel 46, removably fixed to the rotative member 44 of the
gear-blank carrier and meshing with the rack 45.
In this instance, the spur-wheel 46-which practically constitutes a pattern-wheel
for securing, in connection with the rack 45, the requisite ratio of movement between
the gear-blank carrier and cutter-carrier-will, in practice, be of the same diameter
and have the same number and form of teeth as the gear-wheel to be generated.
In the organization thereof shown in Figs. 1 to 5, inclusive, the synchronizing
actuating mechanism S, between the gear-blank carrier and the cutter-carrier, is of
more complex character than the medium shown in Fig. 9; the rack 45 on the
cutter-carrier and the spur-wheel 46 on the gear-blank carrier being shown in
Figs. 1 to 5, inclusive, relatively remote and connected together by means of
suitable intermediate gearing, as by a pinion 48, carried at the inner end of the
driven-shaft 49 and meshing with the rack 45; this shaft 49 being journaled in
suitable bearings on the main-frame and carrying a pinion 50 at the outer end
thereof, which meshes with a large idle-wheel 51 mounted on a stud 52, which is
fixed to an arm 53. This arm is shiftably supported on the shaft 49, and is
adapted for adjustment concentric to the axis of said shaft; an idle-wheel 54 of
relatively-small diameter also being carried on the stud 52, and meshing with the
spur-wheel 46.
When the synchronizing actuating mechanism shown in Figs. 1 to 5, inclusive, is
employed as a connector between the gear-blank carrier and cutter-carrier, it is
necessary to substitute different-sized idle-wheels, as 51 and 54, to adapt the
machine for cutting blanks of different diameters, and so as to maintain the requisite
ratio of velocity between the gear-blank carrier and cutter-carrier; whereas with
the modified form of actuating synchronizing mechanism shown in Fig. 9, it is
necessary to employ a different rack 45 and a different spur-wheel 46 for every
different size of gear-blank to be cut.
To adjust the arm 53, which carries the idle-wheels 51 and 54, so as to permit
large or smaller idle-wheels to be placed in operative relation with the spur-
wheel 46 and the pinion 50, said arm is slotted at 52' at one end thereof concentric
to the axis of movement of said arm; and through this arm is extended a clamping-
bolt 53", which has a screw-threaded bearing in a fixture of the main-frame of the
machine. (See Figs. 2 and 5 of the drawings.) And to facilitate the adjustment
of the idle-wheels longitudinally of the arm 53, said arın has a longitudinal slot 55
through which the stud 52, on which the idle-wheels are mounted, is extended.
This stud is screw-threaded at one end, and furnished with a nut to hold the same
in adjusted position on the arm 53.
In the drawings, (see Figs. 1, 2, 4, and 5,) two separate gear-blanks are shown
carried upon the arbor 40 in position to be operated upon by the multiplex-cutter.
This is optional.
To provide means for clamping the gear-blank on the arbor, said arbor is shown
provided with a peripheral flange at one end, as at 40', and is screw-threaded and
provided with a nut 40" at the opposite end.
As a means for automatically feeding the blank-carrier C transversely of the

page_text: multiplex-cutter C3, at the requisite points in the advancing and retractive move-
ments of said cutter, the sleeve 43, in which the carrier-member 36 is journaled for
rotation, is shown furnished with a rack 56 on the lower face thereof, which
extends longitudinally of said sleeve and meshes with a pinion 57, carried on a
horizontal shaft journaled in bearings in a bracket on the blank-carrier frame F';
Baid shaft being provided at its outer end with a worm-wheel 58, which meshes
with and is actuated by a worm 59, splined for longitudinal movement on a feed-
shaft 60, which is journaled at its lower end on a bracket 601 on the cutter-carrier
frame F; said shaft being held against longitudinal movement by suitable collars.
At the lower end thereof, the feed-shaft 60 is provided with a feed-wheel 61,
(herein shown as a "star-wheel,") having a series of radially-disposed arms 61' in
position to be engaged by abutments on the cutter-carrier C during the forward
and backward movements thereof. The feed-shaft-actuating abutments or stops,
which are designated by 62 and 63, respectively, are adjustably secured to the side
of the cutter-carrier, as shown in Figs. 3 to 5, inclusive, and are located a distance
apart equal to or slightly greater than the peripheral length of the gear-blank to
he cut; one stop, as 62, being located near the rear end of the cutter-carrier so as
to engage and rotate the feed-wheel near the end of the advancing stroke of the
cutter-carrier, to move the gear-blank inwardly relatively to the cutter, and bring
another portion of the gear-blank into position to be operated upon by the cutter,
during the retractive movement thereof; and the other stop, as 63, being located
near the forward end of said cutter-carrier, and actuating the feed-wheel near the
end of the retractive movement of the cutter-carrier.
The reversing-driving mechanism I) for effecting a continuous rotation of the
cutter C³ in one direction, and for alternately advancing and retracting the cutter-
carrier C, during, and without effecting a change in, the rotation of said cutter,
may comprise a pulley 65, fixed to the worm-shaft 35; two loose pulleys 66 and 67,
one at each side of said shaft-pulley; two driving-belts-i.e., a straight-belt 68 and
a twist-helt 69, (shown in dotted lines in Figs. 2 and 4,)-which may lead to the
usual driving-pulley on the main-shaft (not shown;) and which belts are adapted
for rotating the fast-pulley 65, alternately and in opposite directions, when said
belts are shitted on and off said fast-pulley, which may be automatically effected
by means controlled by the movement of the cutter-carrier, as will be hereinafter
described.
As a means for continuously rotating the cutter-actuating shaft 28 constantly in
one direction, and in synchronism with the rotation of the cutter-carrier actuating-
shaft 35-irrespective of the direction of movement of said shaft 35-the shaft 28
has fixed thereon two pinions 70 and 71, located, one adjacent to the outer face of
each loose-pulley 66 and 67, as clearly shown in Figs. 1, 2, 6, and 7; and said
louse-pulleys have, respectively, pinions 72 and 73, fixed concentrically thereto.
The pinion 72 is fixed to the loose-pulley 66, and is geared to the pinion 70 by
means of two intermediate idle-wheels 70 and 72'; and the pinion 73 is fixed to
the loose-pulley 67, and is geared to the pinion 71 by means of one intermediate
idle-wheel 71. Thus, it will be seen that the loose-pulley 66 is in geared connection
with the cutter-actuating shaft 28 by a train of gears adapted for rotating said
shaft with, and in the same direction as, the pulley 66 rotate; whereas the loose-
pulley 67 is in geared connection with the shaft 28, adapted for rotating said shaft
in a reverse direction from that in which said pulley 67 rotates; therefore, not-
withstanding the fact that the louse-pulleys 66 and 67 are rotated alternately in
reverse directions, the direction of the cutter-actuating shait remains unchanged.
Normally, one of the belts extends over the tight-pulley, and the other belt
extends over the loose-pulley; and as a means for automatically shifting said
belts 68 and 69 together or separately, as required for reversing the direction of
rotation of the cutter-carrier-actuating shaft, or for stopping said shaft, belt-shifting
mechanism is provided, which, in the form shown most clearly in Figs. 6, 7, and 8,
comprises suitable shipper-levers 75 and 76, which engage the belts 68 and 69,
respectively. These shipper-levers are carried at their lower ends upou rock-

page_text: shafts 75 and 761, journaled in suitable bearings on the main-frame F, and having
cranks 75 and 76 at the opposite ends thereof with projections engaging in cam-
slots 771 and 781, formed in shipper-cams 77 and 78, which are supported for sliding
movement in a suitable slideway 79 on the frame F of the machine.
The instrumentality preferably employed for operating the shipper-cams 77
and 78, is shown consisting of a horizontal actuating-rod 80, journaled for sliding
and rocking movement in suitable bearings in the frame F; said actuating-rod
being provided with two transverse cam-actuating arms 81 and 82, one of which
is adapted when in the position shown in Figs. 4 and 5-for engaging both
cams 77 and 78, and for shifting said cams together in one direction, when the
actuating-red 80 is moved longitudinally in that direction, and the other of said
arms when in this position-being adapted, when the rod is moved in the
opposite direction, for shifting both cams in the reverse direction.
The cam-actuating rod 80 is automatically moved longitudinally by the stops 83
and 84 near opposite ends, respectively, of the stroke of the cutter-carrier; which
stops engage an abutment on a cam-actuating rod 80, and thereby shift the shipper-
cams 77 and 78 together, first in one and then in the opposite direction, thus
actuating the rock-shafts 75' and 76', and throwing the belts 68 and 69 alternately
on and off the tight-pulley 65. This will automatically effect a reversal in the
direction of the movement of the cutter-carrier, without effecting a change in the
direction of rotation of the cutter.
An automatic stopping device is provided for stopping the movement of
the cutter-carrier upon the completion of the tooth-generating operation. This
means, which is automatically controlled by the movement of the gear-blank
carrier C transversely of the cutter C³, consists of a rock-shaft 86, having a
sliding fit in a journal 86' on the blank-carrier frame F', and having its lower end
journaled in a bearing on the cutter-carrier frame F, as shown most clearly in
Figs. 3, 4, and 5; an actuating-arm 87, splined to the shaft 86 between abutments
on the frame F1, and having its outer, free end located in the path of movement
of a projection 88 on the gear-blank-carrier C¹.
This rock-shaft 86 is operatively connected at its lower end with an arm 89 on
the cam-actuating rod 80 by a crank-connection, (designated in a general way by H,)
which may be of any suitable construction for partially rotating the cam-actuating
rod upon a partial rotation of the rock-shaft 86, as will be understood by reference
to Figs. 4, 6, 7, and 8.
This crank-connection is so arranged as to rotate the rod 80 in a direction
required for throwing the cam-actuating arms 81, and 82, downward, so as to
engage only the lower cam upon the longitudiual movement of the cam-actuating
rod 80, as is required for shifting one of the belts, as 68, independently of the
other helt on to the loose-pulley, and thereby stop the rotation of the cutter-
carrier actuating-shaft 35, immediately upon the operation of the automatic
stopping device by the gear-blank carrier.
It is desired to state, in the above connection, that the construction and
organization of the cutter carrier; the mechanism employed for actuating the
cutter and cutter-carrier, and the mechanism employed for automatically reversing
the direction of movement of the cutter-carrier, and for automatically stopping
the cutter-carrier, may be variously modified, within the scope and limit of this
invention; and also that the means for effecting the requisite ratio of movement
between the gear-blank and cutter-carrier may be variously modified, without
departure from my invention.
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. A machine for generating gear-teeth, embodying a rotative gear-blank; a
rotative cutter; and means for rotating the gear-blank, and for moving the cutter
along the periphery of the gear-blank in the same direction and at the same

page_text: peripheral velocity, whereby a portion of every tooth of the entire circuit of teeth
is generated at one cutting operation.
2. The herein-described instrumentalities for generating gear-teeth in a gear-
blank by moving a cutter along the periphery of the gear-blank in the same
direction and at the same peripheral velocity, and cutting portions of the entire
circuit of teeth at one stroke of the cutter.
3. In a machine for generating gear-teeth, carrying and rotating means for a
gear-blank; in combination with a multiplex-cutter of a length not less than the
peripheral length of the blank to be cut; a movable cutter-carrier; and means
actuated by the cutter-carrier for rotating the blank-carrier.
4. The combination of a rotative gear-blank carrier; a reciprocative cutter-
carrier supported in operative relation with the gear-blank carrier, a rotative,
multiplex-cutter carried by said carrier, and having its effective stroke of a length
not less than the peripheral length of the gear-blank in which the teeth are to be
generated; synchronizing actuating mechanism for rotating the gear-blank and
cutter, and for imparting to the cutter an endwise working-stroke of a length not
less than the peripheral length of the gear-blank in which the teeth are to be
generated, at each complete rotation of the gear-blank carrier, and in the direction
of rotation of the gear-blank carrier, and at right-angles to the axis of said
carrier.
5. The combination of a reversibly-rotative gear-blank carrier; a reciprocative
cutter-carrier; a rotative, multiplex-cutter carried by said cutter-carrier; actuating
mechanism for synchronously rotating the gear-blank carrier, first in one direction
ther in the opposite direction, and for simultaneously rotating the multiplex-cutter,
and at the same time moving the same longitudinally at a velocity corresponding
substantially with the pitch-line velocity of the blank in which the teeth are to be
generated, and first in one and then in the opposite direction, coinciding with the
directions of movements of the blank-carrier; and means controlled by the move-
ments of the cutter-carrier for automatically changing the relative transverse
relations of the gear-blank carrier and cutter-carrier.
6. A. machine for generating gear-teeth, comprehending a multiplex-cutter of a
length not less than the peripheral length of the gear-blank in which the teeth are
to be generated; a carrier for the gear-blank; actuating mechanism for imparting
to the cutter and gear-blank a motion corresponding to the motion of a rack and an
intermeshing, rotating pinion, and for moving said cutter a distance not less than
the peripheral length of the gear-blank at each stroke of the cutter and at each
complete rotation of the gear-blank; means for continuously rotating the
multiplex-cutter; and feeding mechanism for automatically changing the relative
transverse relation of the gear-blank and cutter, intermediate to successive cutting-
strokes of said cutter.
7. In a machine of the class specified, a rotative gear-blank carrier and a
reciprocative cutter-carrier, supported one above the other, with their axes of
movement in planes intersecting each other; in combination with means for
reciprocating the cutter-carrier; and an actuating-connector between and operatively
connecting, the gear-blank and cutter-carrier, and adapted for rotating the gear-
blank carrier in synchronism with the movements of the cutter-carrier, and for
establishing a predetermined ratio of movement between said cutter-carrier and
gear-blank carrier.
8. A machine for generating gear-teeth, comprehending an axially-rotative cutter
of a length not less than the peripheral length of the blank to be cut; a rotative
gear-blank-carrying member and a reciprocative cutter-carrying member, one of
which carrying members is in operative connection with, and is directly actuated
by, the other in the same direction, and at comparative velocities of a predetermined
ratio; and means for actuating one of said members.
9. A machine for generating gear-teeth, comprehending a reversibly-rotative
blak-carry ing member; a reciprocative cutter-carrying member in direct geared-

page_text: connection with the blank-carrying member, and having the plane of its movements
transverse to the axis of rotation of the blank-carrying member; and a rotative
multiplex-cutter carried by the cutter-carrying member; actuating means for
reciprocating the cutter-carrying member; and means for rotating the cutter
simultaneously with the reciprocatory movement of the cutter-carrying member,
substantially as described.
10. In a machine for generating gear-teeth, a rotative gear-blank-carrying
member, and a reciprocative cutter-carrying member, one of which is in operative
connection with, and is directly actuated by, the other; means for actuating one
of said members; and means controlled by one of said members for changing the
relative transverse relations of the two members, substantially as described, and for
the purpose set forth.
11. In a machine for generating gear-teeth, a rotative carrier for the gear-
blank; a cutter-carrier supported for longitudinal movement in a plane transverse
to the axis of the gear-blank carrier; a longitudinally-disposed rack on the
cutter-carrier; a spur-wheel on the gear-blank carrier in geared connection with
the rack on the cutter-carrier; and actuating mechanism for imparting longitudinal
movements to the cutter-carrier, substantially as described, and for the purpose
set forth.
12. In a machine for generating gear-teeth, a rotative gear-blank carrier, and a
longitudinally-movable cutter-carrier supported with their axes of movement in
relative transverse planes; a rack on the cutter-carrier; a pinion on the gear-
blank carrier in geared connection with the rack on the cutter-carrier; a rotative
multiplex-cutter carried by the cutter-carrier with its axis of rotation transverse to
the axis of the gear-blank carrier; actuating mechanism for imparting longitudinal
movements to the cutter-carrier; rotating mechanism in connection with the
cutter; and feeding mechanism for effecting a change in the transverse relations
of the gear-blank carrier and cutter, substantially as described, and for the purpose
set forth.
13: In a machine for generating gear-teeth, a rotative gear-blank carrier; a
multiplex-cutter supported for rotation in longitudinal movement below, and with
its axes in a plane at right angles to, the axis of the gear-blank; reversing-driving
mechanism for rotating the cutter continuously in one direction, and for moving
the same longitudinally first in one and then in the opposite direction; and
actuating mechanism for rotating the gear-blank carrier, first in oue direction
and then in the opposite direction, in synchronism, and coinciding with the directions
of movements of the cutter, to establish a uniform peripheral velocity between the
cutter and the gear-teeth in which the teeth are to be generated.
14. In a machine for generating gear-teeth, a rotative gear-blank carrier; a
reciprocative cutter-carrier having its plane of movement transverse to the axis of
the gear-blank carrier and a rotative multiplex-cutter; in combination with
reversing-driving mechanism in connection with, and adapted for moving, the cutter-
carrier longitudinally, first in one and then in the opposite direction; cutter-rotating
mechanism in connection with, and adapted for continuously rotating, the cutter ;
gearing intermediate to, and operatively connecting, the reversing-driving
mechanism and the cutter-rotating mechanism; synchronizing actuating mechanism
intermediate to, and operatively connecting, the gear-blank carrier and cutter-
carrier, and adapted for establishing a predetermined ratio of movement between
the gear-blank carrier and the cutter-carrier; and feeding mechanism controlled by
the longitudinal movements of the cutter-carrier for effecting a change in the
transverse relation of the gear-blank carrier and 'cutter-carrier, substantially as
described, and for the purpose set forth.
15. In a machine of the class specified, the combination of a cutter-carrier
frame; a cutter-carrier supported for longitudinal movement on said frame; a
rotative multiplex-cutter carried on said cutter-carrier with its axis in the plane of
longitudinal movement of the cutter-carrier; a gear-blank-carrier frame supported

page_text: on the cutter-carrier frame for adjustment vertically thereof; adjusting means for
said blank-carrier frame; a rotative gear-blank carrier supported on the blank-
carrier frame with its axis transverse of the path of movement of the cutter-carrier;
and actuating mechanism for synchronously moving the gear-blank carrier and
cutter-carrier, the first rotatively and the other longitudinally in the same direction
and at comparative velocities of a predetermined ratio.
16. In a machine of the class spécified, the combination of a cutter-carrier frame;
a horizontally-disposed cutter-carrier supported for longitudinal movement upon
said frame; a multiplex-cutter rotatively carried ou the cutter-carrier with its axis
in the plane of the longitudinal movement of the cutter-carrier and transversely of
a gear-blank carrier; a gear-blank-carrier frame supported on the cutter-carrier
frame for adjustment vertically thereof; adjusting means for said blank-carrier
frame; a rotative gear-blank carrier supported on the blank-carrier frame, with
its axis transverse to the path of movement of the cutter-carrier, and for adjust-
ment transversely of the multiplex-cutter; synchronizing actuating mechanism
operatively connecting the gear-blank carrier and cutter-carrier, and controlled by
the movements of the cutter-carrier for establishing a predetermined ratio of
movement between the gear-blank carrier and cutter-carrier; actuating mechanism
in connection with, and adapted for moving, the cutter-carrier and the cutter thereon
transversely of the plane of the axis of the gear-blank carrier; rotative mechanism
for the cutter; and means controlled by the movement of the cutter-carrier for
intermittently feeding the gear-blauk carrier transversely of the cutter.
17. In a machine for generating gear-teeth, a rotative gear-blank carrier, and a
longitudinally-movable multiplex-cutter supported with their axes in a plane
transversely of each other; in combination with actuating mechanism for rotating
the cutter, and for simultaneously moving the cutter longitudinally, and the gear-
blank carrier rotatively, in the same direction at comparative velocities of a
predetermined ratio; reversing mechanism for intermittently reversing together
the longitudinal and rotative directions of movements of the cutter and gear-blank
carrier, respectively; feeding mechanism controlled by the longitudinal movements
of the cutter for automatically and intermittently moving the gear blank carrier
transversely of said cutter; and a stopping mechanism controlled by the movements
of the gear blank carrier transversely of the cutter, for automatically stopping the
longitudinal movement of the cutter at a predetermined point in said relatively-
transverse movement of the gear-blank carrier.
18. In a machine for generating gear-teeth, the combination with a rotative gear-
blank carrier adapted for carrying the gear-blank in which the teeth are to be
generated; of a rotative, multiplex-cutter supported for movement in the plane of
its longitudinal axis and transversely of the axis of the gear-blank carrier, and
comprehending a multiplicity of relatively transversely-separated polygonal cutters,
in axial alignment and of an aggregate cutting length, longitudinally of said axis,
not less than the peripheral length of the gear-blank in which the teeth are to be
generated; a cutter-carrier; and means connecting said carriers, substantially as
described.
19. A rotative multiplex-cutter of a length not less than the peripheral length of
the blank to be cut, and a movable cutter-carrier in combination with a gear-blank
carrier; and mechanism connecting said carriers.
20. A rotative multiplex-cutter of a length not less than the peripheral length
of the blank to be cut, and a movable cutter-carrier in combination with a gear-blank
carrier; mechanism connecting said carrier; and means for moving one of said
carriers transversely.
21. A gear-tooth-generating machine comprehending an axially-rotative
multiplex-cutter of length not less than the peripheral length of the blank
to be cut; a carrier by which said cutter is supported; a gear-blauk carrier;
and intervening means connecting the two carriers, and by which one carrier is
actuated by the other carrier.
22. A movable carrier, and a multiplex-cutter of a length not less than the

page_text: peripheral length of the blank to be cut, carried thereby; in combination with a
gear-blank carrier; means for moving one carrier transversely with relation to the
other; and gearing connecting said carriers.
Dated this 2nd day of April A.D. 1896.
HERBERT CURTIS WARREN.
Haseltine, Lake & Co.,
45 Southampton Buildings, London, W.C., Agents for the Applicant.