Improvements in Apparatus for Cutting Gear Teeth.
Year: 1895

page_text: Date of Application, 8th Oct., 1895-Accepted, 23rd Nov., 1895
COMPLETE SPECIFICATION.
Improvements in Apparatus for Cutting Gear Teeth.
I. HERBERT CURTIS WARREN, of No. 283 Collins Street, in the City and
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 machines for generating gear-teeth of various kinds,
the object of my present invention bing to primarily furnish an improved
apparatus, or machine, whereby theoretically-correct gear-teeth, and more
especially, radial gear-teeth may be generated with rapidity and economy, and
without the use of a pattern-templet; and also to so construct and organize the
different mechanisms of the apparatus, or machine, as to readily adapt the same for
generating gear-teeth of different size, and contours, as required for gears of
different sizes and kinds.
My improved machine for generating gear-teeth, in accordance with my present
invention, embodies a gear-blank carrier; means for rotating said gear-blank
carrier to bring successive tooth-space-forming portions of the gear-blank into
position to be successively acted upon by the cutter; a revoluble cutter; a cutter-
carrier; means for effecting a progressive, forward movement of the cutter along
the tooth-forming portion of the gear-blank intermediate to said partial rotation
of said blank, and in a plane coinciding with the plane of the tooth-face being
generated; and means for effecting simultaneous rotary reciprocating movements
of the gear-blank carrier and cutter-carrier, whereby theoretically-correct gear-
teeth are generated by progressive, sinuous movements of the cutter, all of which
will be hereinafter described, and more particularly pointed out in the claims.
In the drawings accompanying and forming part of this Specification,
Figure 1 is a plan view of a machine, or apparatus, for generating gear-teeth in
accordance with my present invention; said figure showing the gear-blank in
position to be operated upon by the tooth-generating cutters.
Fig. 2 is a side elevation of the machine, as seen from the under side in Fig. 1;
parts thereof being shown in their normal, inoperative positions, or in the positions
they occupy, just preparatory to effective operations of the cutters upon the gear-
blank.
Fig. 3 is a view, similar to Fig. 2 of the machine, as seen from the upper side,
Fig. 1.
Fig. 4 is a vertical, longitudinal section of the machine, taken in dotted line a-a,
Fig. 1, and looking in the direction of the arrow in said figure.
Fig. is a horizontal cross-section of a portion of a machine, taken in dotted
line b-b, Fig. 4.
Fig. 6 is a transverse, vertical section of the machine, taken in dotted line c―c,
Fig. 2, as seen from the right hand in said figure.
Fig. 7 is a transverse, vertical section, taken in dotted line c-c, Fig. 2, as seen
from the left hand in said figure.
Figure 8 is a sectional, side elevation, similar to Fig. 3, of a portion of the
machine, showing the oscillating mechani-m for the cutter-carrier and the gear-
blank carrier, in one extreme position thereof; the cutter-carrier and its supporting
means being removed.
Fig. 9 is a cross-sectional view, taken in dotted line c-c. Fig. 2, looking toward
the lett in said figure, and showing the cutter-carrier and co-operating parts in the

page_text: positions they occupy, when the oscillating mechanism therefor is in the position
shown in Fig. 8.
Fig. 10 is a sectional, side view, similar to Fig. 8, of a portion of a machine,
showing the oscillating mechanism for the cutter-carrier and the gear-blank carrier
in another extreme position, opposite to that shown in Fig. 8.
Fig. 11 is a cross-sectional view of the machine, similar to that shown in Fig. 9,
and showing the position occupied by the cutter-carrier, when the blank-carrier is
in the position shown in Fig. 10.
Fig. 12 is a sectional, front elevation, on a relatively-large scale, of a portion.
of a cutter-carrier and its supporting means; said figure showing the portion of
the rotating means for one of the cutters, and also showing in section the means for
effecting the transverse adjustment of the cutter, relatively to the cutter-slide.
Fig. 13 is a longitudinal section of the parts shown in Fig. 12, taken in dotted
line d-d, said figure, and looking toward the left hand in said Fig. 12.
Fig. 14 is a cross-sectional view of the parts shown in Fig. 12, taken in dotted
line e-e, and looking from the upper side, in said Fig. 12.
Fig. 15 is a front view of one of the cutter-slides detached.
Fig. 16 is a side view of said cutter-slide.
Fig. 17 is a front view of the cutter-slide carrier, for the cutter-slide shown in
Fig. 15.
Fig. 18 is a side elevation of said cutter-slide carrier.
Fig. 19 is a plan view of said cutter-slide carrier, drawn in projection with Fig. 17.
Fig. 20 is a horizontal cross-section of a portion of the frame-work of the
machine and a portion of the cutter-carrier-oscillating mechanism, taken in dotted
line, Fig. 3, and looking from the upper side in said figure.
Fig. 21 is a front view of the oscillatory member of the cutter-carrier actuator,
hich member also constitutes a support for the cutter-carrier.
Fig. 22 is an edge view of said oscillatory member, as seen from the left hand in
Fig. 21.
Fig. 23 is a side view of the reciprocatory member of the cutter-carrier actuator,
which member co-operates with the oscillatory member shown in Fig. 21.
Fig. 24 is an edge view of the said reciprocatory member, as seen from the right
hand. Fig. 23.
Fig. 25 is a plan view of said reciprocatory member, drawn in projection with
Fig. 23.
Fig. 26 is a side view, as seen from the left hand, Fig. 9, of the transverse-bar,
for actuating the reciprocatory member of the blank-rarrier actuator.
Fig. 27 is an edge view of sail transverse-bar, as seen from the right hand in
Fig. 26.
Fig. 28 is an end view of said transverse-bar, drawn in projection with Fig. 26.
Figs, 29, 30, and 31 are side, end, mai elge views, respectively, of the qui le-block
for the transverse-bar, which also constitutes a swivel-connection between the
transverse-bar and the recipruestory member of the blank-carrier actuator.
Fig. 32 and 33 are plan and side views, respectively. of the reciprocatory
member of the blank-carrier actuator.
Fig. 34 is a front view, on a relatively-small scale, of a portion of the cutter-
carrier and frame-work, similar to Fig. 12, and showing the cutter-carrier in the
position illustrated in Fig. 11, and also showing, by dotted circles, several successive
positions of one part of the cutter-slide, relatively to the tripping-plate of the
automatic stopping mechanism.
Figs. 35 to 38, inclusive, are operative plan views of a portion of a feeding
mechanism for the cutters, showing four sucressive positions of the star-wheels, or
feed-wheels, of said feed mechanism, relatively to the feed-wheel actuator, coinciding
with the
our steer sive rositions of the entierenartier.
F 59 and 40 are side and the view vetively, of the gear-bund, showing,
infot, lines, several successive po has the cuttins, relatively to the
blank uripe the progressively forwant movement of said cutters.

page_text: Fig. 41 is a diagrammatic view, illustrating the operation of generating the
opposite sides of two adjacent teeth, by two cutters having sinuous movements ;
said figure showing, by dotted lines, seven successive, angular positions assumed by
the cutters in generating a tooth-face; and
Fig. 42 is a diagrammatic view, illustrating the sinuous path described by the
cutters in generating a tooth-face.
In generating gear-teeth, in accordance with my present invention, the conical
gear-blank G, which will, of course, be of the requisite size for producing a
finished gear-wheel of the desired size, will be intermittently and progressively
advanced, rotatively, a tooth-arc distance, at each movement thereof, to bring the
tooth-forming portions of the blank successively into position, to be acted upon by
the cutter and at the completion of each intermittent rotative movement of said
blank G, the cutter will be fed progressively forward, along the tooth-forming face
of the gear-blank, toward the geometrical apex of said blank, and in the plane of
the toth-face being cut and, during the progressive cutting operation of the
cutter, said cutter will be oscillated in a pline transverse to the axis of the said
gear-blank, and the gear-blank will, preferably, be reciprocated, rotatively, in
synchronous, and in a coinciding, direction with the cutter, to effect a rolling action
of the cutter, in lines transversely of the plane of the forward movement of the
cutter; and, thereby generate, by a sinuous cutting operation, a theoretically-
correct tooth-face, all of which will be hereinafter more fully described.
As an instrumentality for generating gear-teeth, in accordance with my present
invention, I have shown in the drawings, a theoretical adaptation of mechanism,
for automatically effecting the requisite movements of the gear-blank and cutter,
the one relatively to the other, to produce theoretically-correct gear-tecth, by
progressive, sinuous cutting operations.
In the preferred organization thereof herein shown and described, the apparatus
for generating gear-teeth, embodies, in part, a rotary-reciprocating or oscillating
cutter-carrier, (designated in a general way by C2;) and a rotary-reciprocating or
oscillating gear-blank carrier (designated in a general way by C³) actuating
mechanism, in connection with, and adapted for synchronously reciprocating, the
cutter-carrier and gear-blank carrier, rotatively, about fixed axes, respectively,
which axes radiate from a common center, or intersect each other. This actuating
mechanism embodies a cutter-carrier actuator; a blank-carrier actuator;
synchronizing actuating-connector between said cutter-carrier actuator and blank-
carrier actuator; feeding mechanism controlled by the reciprocative movements of
the cutter-carrier, and adapted for automatically and intermittently moving the
cutter-carrier forward, in the plane of the tooth being generated; and rotating
and indexing mechanisms, in operative connection with, and adapted for controlling
the movements of, the gear-blank carrier, all of which will be hereinafter more
fully described.
2
Owing to the fact that the spaces between teeth in bevel-gears are of gradually-
reduced width toward the apexes thereof, it is not only desirable, but it is also
conducive to theoretical correctness, in generating teeth of this class, to form only
one face of a gear-tooth at one time, and to employ a relatively-thin cutter adapted
for freely passing through the narrowest part of the tooth-space; and, for this
purpose, and also for the purpose of facilitating the operation of generating a full
complement of gear-teeth in the gear-blank, and to obviate the necessity of a
repetition of operations, to form the opposite working-faces of the successive teeth,
I preferably employ, in connection with the organization of mechanism illustrated
in the drawings, a plurality of tooth-face generating-cutters, (herein shown as
circular milling-cutters, and two in number,) in position and adapted for generating
the opposite faces of adjacent teeth, one cutter (designated by (,) acting and
generating one face of one tooth, and the adjacent cutter (designated by D,) acting
upon, and generating the opposite face of the next adjacent tooth, as will be
understood by reference to the diagrammatic view, Fig. 41, which illustrates the
operation of generating the tooth-faces of a bevel-gear.

page_text: It is desired to state in the above connection, however, that in generating
parallel teeth such, for instance, as the teeth of spur-wheels-it is practicable to
form, simultaneously, or substantially simultaneously, the adjacent faces of two
adjacent teeth, by means of a single cutter having a sinuous cutting movement;
therefore, do not desire to limit this invention to the employment of any
particular number of cutters, or to the specific organization thereof, shown in the
drawings.
It will be understood, that the employment of a plurality of cutters is simply for
the purpose of facilitating the operation of forming gear-teeth, as it enables me to
form a full complement of gear-teeth in a blauk, at substantially each complete
rotation of said blank, which would not be the case, if a single cutter was employed,
although it may be desirable, in some cases-as when generating teeth for very
small gear-wheels-to employ but one cutter.
The frame-work of my improved machine, which frame-work may be of any
suitable, general construction adapted for carrying the operative parts, consists,
in the preferred form thereof herein shown, of a base B; a cutter-mechanism
frame B; the blank-mechanism frame B2; and a bracket, or supplemental-frame B³
for sustaining the actuator.
The two frames B1 and B2, (the frame B' of which constitutes a guiding-support
for the cutter-carrier and its co-operating mechanism, and the frame B2 of which
constitutes a guiding-support for the gear-blank carrier,) are herein shown having
segmental guideways 1 and 1', respectively, in rectangular disposition, relatively
to each other, and having their geometrical axes in substantially-corresponding
planes, as will be readily understood by a comparison of Figs. 1 and 2 of the
drawings. The guideway 1 upon the frame B₁ is in the nature of a parti-circular
guide-bar upon the upper end of a vertically-disposed arm of the frame B', which
bar is adapted for supporting the oscillatory member of the cutter-carrier C³, as
shown most clearly in Figs. 12 and 13, and which will be hereinafter more fully
described; whereas, the guideway 1 of the frame B is shown approximately semi-
circular, and is formed upon the side face of a correspondingly-formed upright
portion of the frame B2, as will be understood by reference to Figs. 4 and 6.
In the organization thereof herein shown and described, the gear-tooth-
generating mechanism embodies two rotative cutters (designated by C and D,
respectively,) supported, side by side, for oscillatory reciprocatory movement
about, and concentric to, a common center, which common center is represented by
a Cotted circle, (designated by g, Fig. 2,) and is represented by the horizontal
dotted line, Fig. 4.
2
!
As a convenient means for supporting the cutters Cal D, el also as a means
for facilitating the adj istment of said cuts, re
relatively to each other, said cutters
are candel by illes or arbon-
tively, rotatively carried in
externally screw-threaded sleeves 2 B², respectively, supported f
adjustment in transverse inprimes
respectively, which slides are adjustar
the commni
and a' upon the entter- lies 4 and 5,
ly support il for movement transversely of
with the cutting-phone of the cutter,
rul 7,
by aid ways and 7 upon the catt
respectively.
1: 1
*
As a convenient means for oscillating the enters in a path excentric to their
common axis g, and also as a convenient means for changing the relative angles of
said cutters, the cutter-slide carriers, or radiu--bars 6 and 7, are pivotally
supported, at their lower ends, so as to oscillate upon a common axis, which axis
is herein shown as a pivot-rod 8, journaled in, and extending through horizontal
bearings in the frame B₁; and said cutter-slide carriers, or radius-bars, are
adjustably connected, at their ends, with a laterally-projecting curved arm or har 9
upon the upper end of a rocking arm or oscillating member 10, which is also
pivotally supp rind, at its lower cid, upon the pivot-rod 8, as is clearly illustrated
in Fig 1 to 1, inclu ive.

page_text: oscillatory member or rocking arm 10, and the direct supporting means for the
cutters, practically constitute the cutter-arrier, in the organization of mechanison
shown in the drawings; but, it will be understood, however, that the ter
"cutter-carrier," in the bra fer sense thereof, as employel in the claims herein,
signifies any form of cutter-carrier embodying one or more cutter-slides, ant
which is a lipted for oscillating the cutter, in the manner here'n describe l.
'
For convenience in pivotally supporting the cutter-slide carriers 6 and 7,
concentrically, said carriers have, at their lower adjacent corners, transversely-
extended pivot bearings 6" and 7, respectively, one of which, as 6, extends int
the other, as 7, and is also supported upon the pivot-rod 8, as shown most clearly
in Fig. 4 of the drawings. This construction and organization enable me to adjust
the cutter-slide carriers radially and in lepen lently.
As will be seen by reference to Figs. 4, 12, and 13, the cutter-slide carriers have
sliding arings at their upper edges up n the periphery of the segmental guide 1,
and are held against lateral displacement by the curved bar 9, at the upper end of
the oscillating member 10, which has a sliding bearing against the opposite side
free of the guide-bar 1, as shown in Figs. 4 and 13. This curved bar is transversely
and longitudinally slotted, as shown at 12, at opposite ends thereof, to receive the
la-crews 13, which extend through said slots, and adjustably secure the cutter-
slude carrier to said curved har 9.
The automatic feeding and oscillating mechanism and the rotating mechanisın
for the cutters will be hereinafter explicitly described.
The gear-blank carrier, is, in the present instance, in the nature of a blank-
carrier spindle 16, journaled for rotation in a cylindrical bearing or externally
screw-threaded sleeve 17, supported for longitudinal adjustment in bearings 18
and 18' upon a blank-carrier-adjusting-slide 14, which slide is preferably segmental
in form, and is adjustably secured to the guideway 1 of the blank-mechanism
frane B2 by means of bolts 14', extending through a substantially-semi-circular
slot in, and concentric to, the substantially-semi-circular guideway 1 of said
means for adjusting the sleeve 17, together with the blank-carrying
spindle 16, radially, to move the blank G toward or from the cutters (and D, a
ut 19 is fitted to the screw-threaded sleeve 17, preferably between the adjacent
ends of the bearings 18 and 18'; and by turning said nut, the requisite radial
adjustment of the blank-carrying spindle is effected, as will readily be understool
by reference to Fig. 4 of the drawings.
trame.
As a
As a convenient means for intermittently rotating the blank-carrying spindle 16,
aid for registering the blanks carried thereby, said spindle is preferably provided,
at the outer end thereof, with a worm-whee! 20, which meshes with, and is rotated
by, a worm 21, whose shaft 22 is journaled in bearings 221 upon a bracket 23,
fixedly clamped upon an oscillating member 24 upon the blank-carrying spindle 16;
a worm 21, being preferably rotated by and through the medium of the rotative
member of a registering device, (desiguated in a general way by R,) which
registering device will usually consist of a fixed, perforated registering-plate 26 and
a register-pin 27, adapted for entering the holes of the registering-plate, and which
pin is carried by the shaft of the worm 21.
It will be obvious, that any suitable registering device may be employed, in
connection with the rotating means of the blank-carrying spindle 16.
As a convenient means for centering, and for securely holding the blank G in
place, in the spindle 16, said spindle is longitudinally bored, from end to end, and
is conically tapered at the inner end of said bore, as shown at 28, to receive the
correspondingly-tapered hub 29 of the blank G, which hub is axially bored, and
internally screw threaded, t receive the screw-threaded inner end of a bolt 30;
the outer headed end of which bolt bears against the outer end of the spindle 16,
as will be understood by reference to Fig. 4 of the drawings. This means for
centering and holding the blank, relatively to the spindle, may, of course, be
modified, within the scope and limits of my invention.

page_text: In the organization of mechanism herein shown and described, and as will be
seen by reference to Figs. 4 and 6 of the drawings, the blank-carrying spindle is
adapted for adjustment in the are of a circle about a geometrical axis, which lies
at the point of intersection of the axial line of the spindle 16 and the axial line of
the pivot-rod 8, about which the cutters oscillate. This enables a change to be
made in the angle of the axis of the blank-carrying spindle, relatively to the
cutting-plane of the cutters C and D, as is necessary to adapt the machine for
generating the different kinds of gear-teeth; and the blank-carrying spindle and
cutter-carrier are adapted for synchronous oscillations, or rotary reciprocations,
transversely of the longitudinal axis of the blank-carrying spindle, as will be
hereinafter more fully described.
As a convenient means for synchronously oscillating, or rotatively reciprocating,
the cutter-carrier and blank-carrier; also for securing comparative movements of
relatively-varying velocities and of a predetermined ratio between said cutter-
carrier and blank-carrier; and also as a means for arbitrarily changing the ratio
of movements between the cutter-carrier and blank-carrier with precision, to
facilitate the generation of different forms and sizes of gear-teeth, I preferably
employ a cutter-carrier actuator, in practically-direct operative connection with the
cutter-carrier; a blank-carrier actuator in operative connection with the blank-
carrier; and a synchronizing actuating-connector between, and operatively
connecting, the cutter-carrier actuator and the blank-carrier actuator, and adapted,
through operative mechanisin hereinafter described, for effecting synchronous
movements of, and also for effecting a change in the relative velocities of, said two
actuators. The cutter-carrier actuator, in the preferred form thereof herein shown,
comprises a vertically-oscillating sector, or seginental gear 31, which constitutes a
part of the oscillatory member 10 of the cutter-carrier, and a vertically-reciprocating
rack 32, the teeth of which mesh with the teeth of the sector. This preferably
constitutes a part of the slide 33, supported for sliding movement in a guideway 34
upon a bracket 35, which bracket is a member of the cutter-mechanism frame B';
said slide being held against lateral movement by the gibs in the usual manner.
The blank-carrier actuator, in the preferred form thereof herein shown, comprises
a reciprocatory rack 36, supported in a horizontal slideway 37, which constitutes a
part of the frame-work of the machine, said rack 36 having a movement at right
angles to, and at one side of, the reciprocating rack 32 of the cutter-carrier actuator;
an oscillat ry member 38, supported for oscillatory movement upon a stud 39 ton
the bracket or supplemental-frame B, and having a sector, or segmental-gear 38,
whose teeth mesh with the teeth of the reciprocating rack 36; an oppositely-
disposed segmental rack, or sector 40 in position and adapted for mushing with,
and oscillating, gear, which constitutes our member of a power transmitter,
intermediate to, and oratively connecting, the oscillatory member 38 and the
gear-blank carrier; and a power transmitter terliste to the oscilatory member
and the bancarier, which consists of a shaft :1, urinaring upon the
frame 1,rive-gear upon said halt in me-l: with the segnewal rack 40, n
pinion 12 income with the cylindried haring reve 17, in which the
44-b!nk
, driving 13, rried by the shaft 41, and
meshing with the poi 2, which is of Schwi, matain an
operative cogent with the pinion. and at the same time, provide for the
adjustment of said pinion, relatively to the driving-gear.
The actuating-tonneter, between the cutter-earrier actuator and the blank-
carrier actuator, e nsist, in the form thereof herein shown, of a guide-block 45,
pivotally carried by the reciprocatory rack 36 of the blank-carrier actuitor, and
a traverse-bar 46, having a sliding-bearing in the pivotal guide-block 45, and
pivoted approximately midway of its length, as at 461, upon the slide 33 of the
cutter-carrier actuator; said guide-block and traverse-bar practically constituting a
shiftable connection between the rack 36 of the blank-carrier actuator and the
rack 32 of the cutter-carrier actuator, and controls the relative movement of said
cctuators. This traverse-bar, in its co-operation with the guide-block 15, nets as a

page_text: sliding cam, to reciprocate the rack 36 of the blank-carrier actuator, in synchronism
with reciprocation of the rack 32 of the cutter-carrier actuator.
As a convenient means for changing the inclination of the traverse-bar, relatively
to the plane of movement of the reciprocatory rack 36 of the blank-rarrier actuator,
to increase or decrease the throw of said actuator, as may be required, to secure
the requisite relative movements of the blank-carrier actuator an1 the cutter-carrier
actuator, said traverse-bar is adjustably secur d. at opposite ends thereof, to the
slide 33 of the cutter-carrier actuator. by means of bolts 47 and 47', which extend
through elongated slots 48 an1 481, which are concentric to the pivot-point 46' of
said bar, as will be readily understood by reference to Figs. 8 and 10 of the
drawings; and as a means for securing extreme prevision in the adjustment of the
traverse-bar, and for indicating the position of said bar, the periphery of one end
of said bar is toothed, or is in the nature of a segmental worm-whe, as shown
at 49, and a worm 50 is provided, which meshes, and is adapted for rotatively
moving, said bar to effect the requisite adjustment thereof. The worm 50 has its
shaft journaled in bearings 51 upon the slide 33, and carries, at the outer end
thereof, a hand-wheel 52 by means of which said worm may be rstated, and also
carries a dial 53, which is adapted for coacting with a pointer 54 on said dial, to
indicate the position of the traverse-bar.
The reciprocating mechanism for the slide 33, which mechanism may be of any
suitable organization for imparting the requisite throw to the slile at the desired
velocity, consists, in the form thereof herein shown, of a driven-shaft 55, joarnaled
in suitable bearings 56 and 56' upon the base B of the machine, and carrying a
driving-pulley 57 at one end thereof, which pulley 57 is driven through a belt,
(shown in dotted lines) extending over a driving-pulley 70, revolably carried upon
a supporting member on the frame B¹, concentric to the pivot-bit 8; a bevel-
gear 58, carried at the opposite end of the driven-shaft; a bevel-gear 59, meshing
with the bevel-gear 58, and having a shaft 60 thereo", journaled in suitable bearings
in the side walls of the base B; a gear-wheel 61, carried upon the shaft 60; a spur-
wheel 62, meshing with the gear-wheel 61, and having its shaft 63, journaled in
suitable bearings in the base B; a wheel 64, carried at the end of the shaft 63
below the traverse-bar-carrying slide 33, and a pitman or connecting-rol 65,
pivotally connected at one end, to the lower end of the slide 33, and pivotally and
adjustably connected at its opposite ends to the face of the wheel 64, as will be
readily understood by reference to Figs. 1, 2, and 3 of the drawings.
The rotating mechanism for the cutters C and D), in the preferred form thereof
herein shown, consists of the driving-pulley 70, having the hub 70', supported upon
a cylindrical carrier 71, carried at the outer end of the pivot-rod 8, concentric
thereto, as more clearly illustrated in Figs. 1 and 4; a gear-wheel 72, carried by
the hub of the driving-pulley 70; two similar gear-wheels 73 and 74, having
shafts 73 and 74', respectively, journaled at opposite sides, respectively, of the axis
of the gear-wheel 72 in bearings 75 and 76; two relatively-short shafts 78 and 78',
journaled in horizontal alignment in suitable bearings 79 and 791, at opposite sides
of the cutter-carrying slides 4 and 5, respectively, which shafts 78 and 78' are
operatively connected with the two cutter-carrying arbors 2 and 3. respectively,
preferably by means of two pairs of spiral-gears 80 and 81, respectively, the two
upper gears of the two pairs of gears being earried by the cutter-arbors 2 and 3,
and the two lower gears being carried by the shafts 78 and 78'; and two telescopic
universal connections 82 and 83, one of which, as 82, forms a universal connection
between the two shafts 73' and 78, and the other of which, as 83, forms a universal
connection between the shaft 74' and the shaft 78. These telescopic and unversal
connectors 82 and 83, together with the relatively--hort shafts 73 and 7%, and 74¹
and 781, will, for convenience, be herein referrel to as Hexible hatts," and as a
whole, will be designated in a general way by F and F, respectively.
It will be obvious, that other forms of Hexible driving means for the cutters C
and D may be employed, with ut departure from my inventions, for instance,
the well-known "Morse" flexible shafting may be practically used in lieu of the

page_text: telescopic universal. haftings, shown in the drawings, as it is simply necessary to
employ driving insan, which will accommodate itself during operation to th
various sitions assumed by the cutters and cutter-slides.
As a nvenient means for intermittently and automatically feeding the cutters C
and D progressively forward along the tooth-forming face of the blank, toward
the apex of said blank, the cutter-slides 4 and 5 are furnished with fe d-screws 85
and 86, respectively, which have screw-threaded hearings in the cutter-slides, and
are rotatively supported, at their upper ends, in the bearings 87 and 88 upon the
slide-carrying radius-bars 6 and 7, respectively, which screws are intermittently
rotated, through the medium of star-wheels 89 and 90, carried at the upper ends
of the screws 85 and 86, respectively, which star-wheels are in position and adapted
during successive operations of the cutter-carrier, for alternately engaging
abutments 91 and 92, respectively, carried at the upper end of the blank-mechanism
frame B, which abutments are projected into the path of movement of the arms
of the star-wheels, and are adapted for effecting a partial rotation of the feed-
screws 85 and 86, alternately at each throw, or movement of the cutter-carrier, as
will be understood by reference to Figs. 1 and 3, and Figs. 35 to 38, inclusive;
said Figs. 35 to 38, inclusive, showing four successive positions of the star-wheels,
relatively to the abutments through which they are rotated.
As a means for simultaneously rotating the two feed-screws of the cutter-li les,
at each partial rotation of one or the other star-wheels, and at the same time,
provide for lateral adjustment of the cutter-carrier slides, relatively to each other,
said feed-screws are operatively connected for synchronous movements, preferably
by means of a universal shaft s, having a sliding fit at opposite ends, and bearings 93
and 94 upon the two slide radius-bars or slide-carriers 6 and 7, and carrying spiral-
gears 96 and 97, at opposite ends thereof, which mesh with similar spiral-gears 96¹
and 97 upon the upper ends of the screws 85 and 86, respectively; said gears 96
and 97 being preferably splined to the shafts, intermediate to the two parts of
the bearings 93 and 94, as will be seen by reference to Figs. 12 and 13.
The abutments 91 and 92, which co-operate with the star-wheels or feed-
wheels 89 and 90, are herein shown in the nature of pins adjustably secured in a
T-shaped guide-slot 98, formed in the upper face of the bracket 99, which constitutes
a part of the blank-mechanism frame B2, as clearly shown in Figs 1 and 2 of the
drawings.
By the construction and organization of mechanism, herein shown and described,
it will he seen that the cutters C and D are constantly rotated, during the
synchronous oscillations of the cutter-carrier and the blank-carrier; and at each
semi-oscillation, or at each stroke of the entter-carrier, the cutters will be simul-
taneously and automatically advanced an arbitrary distance, relatively to the gr
blank, through the medium of the feed device hereinbefore described, as will be
readily understood by a comparison of the several figures of the drawing.
As a convenient me for automatically stopping the orillat ay and the
advancing movements of the cutter, immediately after the completion of the
working stroke of said cutter, I have provided, in connection with the artu sing
mechanism for the oscillating cutter-carrier, an automatically-rile stopping
devier, control by the meg a vent ot the
stopping device ends clutch device (designated in a poural way by [4) and
an automatically-op crable shifting device, in operative connection with said clutch
device. This stopping device, in the specific organization thereof, herein shown
and described, consists of the two gear-toothed clutch-members 100 and 100', one
of which is carried by the hub of the driven-pulley 57, and the other of which is
carried by the shaft 55; a spring-retracted shifting-lever 101, fulcrumed at 102
upon a base B of the machine, and having a catch 103 at the upper end thereof;
a rocking shifting-lever actuator 104, which is shown in the nature of a rock-shaft,
journaled in bearings 105 and 105 upon the cutter-mechanism frame B', and
having heking-arm 106 at one end thereof, in position atal adapted for engaging
a catch 100

page_text: when the clutch-members are in operative engagement with each other; and, said
shaft also having at the opposite cul thereof, an oppositely-lisposed tripping-
arm 107, whose outer end lies in the path of movement of one of the cutter-slides,
and is adapted to be partially rotated by said cutter-slide, at a predetermined point
in the advancing movement of the cutter, to thereby throw the locking-arm out
of engagement with the catch upon the shifting-lever, which allows the retracting-
spring 108 which has one of its ends connectel with the lawer end of said lever,
and has its other end connected to a fixture upon a base B, to retract the lever,
which throws the two clutch-members out of engagement with each other, and
allows the driven-pulley 37 to run loose, thus immediately stopping the operation
of the cutter-carrier-actuating mechanism, and thereby stopping the oscillatory
movement of the cutter, and also the advancing movement of said cutter, as will
be readily understood by reference to Figs. 1, 2, and 34 of the drawings.
As a means for facilitating the accurate adjustments of the two cutter-slide
carriers, relatively to each other, and for indicating the degree of angle of said
cutter-slide carriers relatively to the axis of the gear-blank carrier, or relatively
to the vertical line intersecting the axis of rotation of the cutter-carrier, the
curved bar 9 of the oscillatory member 10, to which the slide-carrying radius-
bars 6 and 7 are adjustably secured, is furnished with a protractor or indicator, as
shown at 109 at the periphery thereof, adapted to coact with marks or pointers
upon the cutter-slide carriers, for indicating the degree of inclination of the
cutting-faces of the cutters relatively to the axial plane of the blank-carrier, as
will be readily understood by reference to Figs. 1 and 7 of the drawings.
In practice, the guideway 1' for the gear-blank-carrier slide, will also be furnished
with a protractor, as shown at 110, adapted to coact with a fixed point herein shown as
the end face upon the blank-carrier slide, for indicating the degree of inclination
of the blank-carrier relatively to the advancing path of movement of the cutters,
as will be understood by reference to Fig. 1 of the drawings.
By the employment of the peculiarly constructed and organized devices, herein
shown and described, in connection with the cutter-carrier, blank-carrier, and with
the cutter-carrier and blank-carrier actuators, it will be seen that the synchronous
oscillatory movements of said cutter-carrier and blank-carrier may be regulated
with extreme precision to secure the utmost accuracy in co-operation, and that the
throw of the cutter-carrier and blank-carrier may be readily increased or decreased,
within certain limits, to accommodate the machine to the formation of various sizes
of gear-teeth; also that the degree of inclination of the tooth-generating cutter
may be quickly changed, relatively to the axial plane of the gear-blank carrier,
to adapt the cutter for generating teeth of different widths; also that the degree
of inclination of the gear-blank carrier may be quickly changed, relatively to the
advancing path of movement of the cutters, as is necessary in operating upon
different sized gear-blanks; and also that the intermittent, advancing movement of
said cutters may be readily increased or decreased, as required.
In generating a bevel-gear tooth by the improved machine herein shown and
described, (assuming the parts of the machine to be in a position illustrated in
Figs. 1, 2, 3, and 4,) upon the inauguration of the movements of the several
mechanisms, the blank G, together with the cutters C and D) will be reciprocated,
rotatively and synchronously, in substantially-corresponding directions, but usually
at relatively-varying velocities, and at each stroke of the cutter-carrier, the cutters
will receive an advancing impulse, in a direction transverse of the axis of the
blank-carrier, and toward the geometrical apex of the gear-blank G. The cutters,
owing to their oscillatory and intermittently advancing movements, will describe
sinuous path during their cutting operations over the tooth-forming face
of the blank, which path of movement of the cutters is represented by the con-
tinuous sinnous line p, Fig. 42 of the drawings, which figure is a diagrammatic
view, illustrating the sinuous cutting movements of the cutters, and clearly shows
the gradual decrease in the throw of the successive oscillatory movements of the
cutters, as they advance toward the geometrical apex of the gear-blank, which
a
B

page_text: apex is represented by the dotted circle, said figure. During this sinuous
cutting movement, the cutting-face of one cutter, as C, (which cutter preferably
has a V-shaped cutting-edge,) assumes the successive angular positions, represented
by lines a, b, c, d, e, f, g, Fig. 41 of the drawings, relatively to the face h of the
tooth being generated, which change in the positions of the cutter, relatively to
the tooth-face, is effected by the oscillations of the gear-blank and cutter, which
causes a rolling motion of the cutter, relatively to the tooth being generated, and
produces a theoretically-correct tooth-face. Thus, it will be seen, that, contrary
to the usual method of cutting a tooth-face by successive operations, a tooth-face
is generated by a continuous movement of the cutter in a sinuous path; the
oscillations of the cutter and the change in the angular positions of said cutter,
relatively to the tooth being generated, generating a theoretically-correct curve for
the working-face of the tooth.
In Figs. 39 and 40, the cutters C and D are shown in full and dotted lines, in
five successive positions assumed by said cutter relatively to the blank G; the
radial dotted lines t and u, Fig. 40, representing the radial paths of movements of
the cutters C and D toward the apex of the blank; the segmental dotted lines v,
representing the successive transverse or oscillatory paths of movement of said
cutters; and the dotted circle w, representing the oscillatory path, described by
the pitch-line of the blank G synchronously with the oscillatory movement of the
cutters C and D.
In referring to the organization of tooth-generating cutters, shown and
described, it is desired to state, that, while it is preferable-especially when
generating the teeth of very small gear-to employ two rotary cutters, so disposed
relatively to each other and relatively to the gear-blank being cut, as to simul
taneously generate the opposite faces of two adjacent teeth-one of said cutters
generating one face of one tooth, and the other of said cutters generating the
opposite face of the next adjacent tooth-the two cutters may be so disposed
relatively, as to generate the opposite faces of the same tooth, which will some-
times be desirable when generating the teeth of relatively-large gears. It will,
therefore, be understood, that I do not limit myself to the employment of any
particular number of cutters, or to any particular relative disposition thereof,
as one or more cutters may be employed, within the scope and limits of 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. In a machine for generating gear-teeth, rotory-reciprocating gear-blank
carrier; and means for automatically actuating aid gear-blank carrier; in com
bination with a rotary-reciprocating etter-tool carrier; and means for imparting
rotory reciprocating movements to aid cutter-errier in a path transversely of the
longitudinal of, and in mehronian with,ger-blank cerrier, substantially
es described.
2. In a machine for generating eth, in combination, a gear-blank carrier,
calentting-toalin tively compted for synchronous, rotory
reciprocating movement, relevey, Juont : common center; and mens for
imparting rutary-reiprocating 0 ct.. to paid carriers, synchronously,
substantially as described.
3. In a machine for generating gear-teeth, in combination, a gear-blank carrier
supported for rotary-reciprocating movements about its axis; a cutter-carrier
supported for rotary-reciprocating movements in a direction coinciding with the
direction of movement of the gear-blank carrier; a rotary cutter carried by said
cutter-carrier in position and adapted for acting upon the gear-blank carried by the
blank-carrier; and mechanism for actuating said parts synchronously, substantially
ns described.
4. Inching for generating porteeth, in combination. a gear-blank carrier;

page_text: mechanism for imparting to said carrier rotary-reciprocating movements about its
axis; a cutter-carrier; and synchronizing actuating mechanism operatively con-
necting the gear-blank carrier and cutter-carrier, and adapted for imparting
rotary-reciprocating movements to the cutter-carrier transversely of the axis of the
gear-blank carrier, and also for effecting synchronous movements of said cutter-
blank carrier and gear-blank carrier, substantially as described.
5. In a machine for generating gear-teeth, a gear-blank carrier, and a cutter-
carrier, in combination with an actuating-connector between, and adapted for
effecting a synchronous oscillating movement of, said gear-blank carrier and
cutter-carrier, substantially as described, and for the purpose set forth.
6. In a machine for generating gear-teeth, the combination of an oscillatory
gear-blank carrier; an oscillatory cutter-carrier; and carrier-actuating means in
operative connection with, and simultaneously imparting oscillatory movements to,
said gear-blank carrier and cutter-carrier, respectively, in relatively-coinciding
directions.
7. In a machine for generating gear-teeth, in combination, an oscillatory gear-
blank carrier; an oscillatory cutter-carrier; and means in operative connection
with, and adapted for imparting oscillatory movements of relatively-varying
velocities to, said gear-blank carrier and cutter-carrier, synchronously.
8. In a machine of the class specified, the combination with a rotary-reciprocating
blank-carrier; and with means for automatically imparting rotary-reciprocating
movements to said blank-carrier; of a rotary cutter supported for oscillatory
movement; and means for imparting rotating and advancing movements to the
cutter in the plane of its cutting-edge; and means for imparting oscillatory move-
ments to said cutter in synchronism with the rotary-reciprocating movements of
the blank-carrier, substantially as described, and for the purpose set forth.
9. In a machine of the class specified, in combination, a blank-carrier, and a
cutter-carrier operatively connected for synchronous oscillatory movements about
axes radiating from a common center; a rotary cutter carried by the cutter-carrier;
and actuating mechanism in connection with, and adapted for synchronously and
automatically imparting oscillatory movements to, the blank-carrier and cutter-
carrier; and means for rotating the cutter and advancing said cutter toward the
center from which the axes of said blank-carrier and cutter-carrier radiate,
substantially as described and for the purpose set forth.
10. In a machine for generating gear-teeth, in combination, a blank-carrying
spindle; actuating mechanism for automatically imparting rotary-reciprocating
movements to said spindle; a cutter-carrier ; means for oscillating said cutter-
carrier in a plane transversely of the axes of, and in synchronism with, and in a
direction corresponding to the direction of movement of, the blank-carrying
spindle; a rotary cutter movably carried by said cutter-carrier; and a cutter-
carrier rotating and feeding means for rotating said cutter-carrier, and for
imparting advancing movement thereto, in a plane intersecting the axial plane of
said spindle, substantially as described.
11. In a machine of the class specified, the combination of an oscillatory gear-
blank carrier; a rotary cutter supported for oscillatory movement; actuating
means conuecting the gear-blank carrier and cutter, and adapted for imparting
oscillatory movements to the gear-blank carrier, and for simultaneously imparting
to the cutter a progressive cutting movement in a sinuous path transversely of the
axial line of the blank-carrier, substantially as described, and for the purpose
set forth.
12. In a machine for generating gear-teeth, in combination, a gear-blank carrier
adapted for rotary-reciprocating movements about its axis; actuating mechanism
for said gear-blank carrier; a rotary cutter supported and adapted for intermittent
advancing movements in a plane intersecting the axial plane of the blank-carrier;
cutter-actuating mechanism co-operating with the blank-carrier-actuating mechanism
for effecting synchronous operations of said two actuating mechanisms; and means
for intermittently advancing the cutter along the blank carried by the blank-

page_text: carrier in a plane corresponding to the longitudinal plane of the face of the tooth
being generated, and also for oscillating the cutter in a plane substantially
concentric to the axis of the blank-carrier, and transversely of the tooth being
generated, substantially as described.
13. In a machine for generating bevel-gear teeth, in combination, a gear-blank
carrier supported for rotary-reciprocating movements about its axis; a rotary
cutter supported for intermittent advancing movement in a plane intersecting the
axial plane of the blank-carrier, and also for transverse and rotary-reciprocating
movements; cutter-feeding mechanism in connection with, and adapted for
advancing, the cutter along the blank carried by the blank-carrier; and
synchronizing actuating mechanism co-operatively connecting the blank-carrier
and cutter, and adapted for synchronously imparting rotary-reciprocating move-
ments to the blank-carrier and cutter in corresponding directions, substantially as
described, and for the purpose set forth.
14. In a machine for generating gear-teeth, the combination with the oscillatory
gear-blank carrier and its actuating mechanism; of a rotary tooth-generating
cutter in position and adapted for acting upon the gear-blank carried by the blank-
carrier; and cutter-controlling mechanism, substantially as described, in operative
connection with the cutter and with the gear-blank-actuating mechanism, and
adapted for moving the cutter progressively forward along the tooth-forming face
of the gear-blank in a plane corresponding to the longitudinal plane of the gear-
tooth, and for oscillating said cutter transversely of the longitudinal plane of the
gear-tooth in synchronism with the oscillatory movement of the gear-blank carrier,
substantially as described, and for the purpose set forth.
15. In a machine for generating gear-teeth, in combination, an oscillatory holder
for the gear-blank; registering mechanism carried by the gear-blank holder, and
adapted for intermittently rotating the blank-holder an aliquot part of a complete
rotation; a tooth-generating cutter supported for rotary and transverse oscillatory
movements; and gear-blank and cutter actuating and controlling mechanism,
substantially as described, co-operatively connecting the blank-carrier and cutter,
and adapted for synchronously oscillating said blank-carrier and cutter in coinciding
directions and in substantially-concentric planes; and means for moving the cutter
progressively along the tooth-forming face of the gear-blank, during the oscillatory
movement of said cutter, substantially as described.
16. In a machine for generating gear-teeth; an oscillatory gear-blank carrier;
a rotary cutter; an oscillatory cutter-carrier; an actuating-connector between the
gear-blank carrier and cutter-carrier, and adapted for synchronously oscillating
the gear-blank and cutter in coinciding direction, and in planes substantially
concentric to a common center; and means for rotating and advancing the cutter
relatively to the gear-blank, tuntially as described, and for the purpose
set forth.
17. In a machine for generating bevel-gear teeth, in combination, a gear-blank
carrier up the ye
ents hout its axis; a rotary
cutter supported for intermittent dyna ing movement in a plane intersecting the
axial plane of the carrier, and al for from verse and rotary-reciprocating
movement : cutter in connection with, and adapted ior
advancing the cuffer plang th
en by the carrier; and synchru-
nizing netti,rativaly meeting the bank-carrier and cutter,
and adapted for syncionou by parting try-reciprocating movements of
relatively-varying velocities to the blank-carrier and cutter in corresponding
directions, substantially as described, and for the purpose set forth.
18. In a machine for generating gear-teeth, the combination of an oscillatory
gear-blank carrier; and an oscillatory cutter-carrier slide, both supported for
radial movements relatively to a common center; and means, substantially as
described, for simultaneously oscillating the gear-blank carrier and cutter-slide
carrier about said connion center, and for moving said blank-carrier and cutter-slide
carrier radially of said common center for the purpose set forth.

page_text: 19. In a machine for generating gear-teeth, the combination with an inter-
mittently-rotative gear-blank carrier; and with means for intermittently rotating
said gear-blank carrier; of a cutter-slide carrier supported for oscillatory movements
transversely of the gear-blank carrier, and having a cutter-slide supported for
radial movements, relatively to the axis of the cutter-slide carrier; oscillating
mechanism operatively connecting the blank-carrier and cutter-slide carrier, and
adapted for synchronously oscillating said carriers in corresponding directions;
and actuating mechanism, substantially as described, in position and adapted for
intermittently imparting an advancing movement to the cutter-slide, substantially
as described, and for the purpose set forth.
20. In a machine for generating bevel-gear teeth, in combination, a cutter-slide
carrier, and a gear-blank carrier supported for synchronous oscillatory movements
about intersecting axes; and means in operative connection with, and adapted for
synchronously oscillating, said cutter-slide carrier and blank-carrier, substantially
as described, and for the purpose set forth.
21. In a machine of the class specified, an oscillatory blank-carrier, and an
Oscillatory cutter-carrier supported with their axes radiating from a common center,
and adapted for radial and substantially-concentric adjustments relatively to the
common center, from which the axes of said carriers radiate, and for synchronous
oscillatory movements; in combination with independent adjusting means for the
blank-carrier and for the cutter-carrier, and adapted for independently adjusting
said carriers concentrically of, and toward and from, said common center; and
actuating mechanism operatively connecting said carriers and adapted for synchro-
nously oscillating said carriers in corresponding directions, and at relatively-
different velocities, substantially as described, and for the purpose set forth.
22. In a machine for generating gear-teeth, in combination, a cutter-carrier
supported for oscillatory movements about a fixed axis; a rotating cutter supported
for movement radially of the axis of said carrier; means for oscillating said
cutter-carrier; and an oscillatory gear-blank carrier supported for radial and
concentric adjustments, relatively to an axis having an arbitrarily-fixed relation to
the axis of the cutter-carrier; and means for automatically oscillating the gear-
blank carrier in synchronism with, and in a direction corresponding to the
direction of movement of, the cutter-carrier, substantially as described, and for the
purpose set forth.
23. In a machine for generating gear-teeth, the combination with the cutter-
slide carrier supported for oscillatory movement about a relatively-fixed axis, and
with the cutter-slide and the rotating cutter supported for radial movement,
relatively to the axis of said cutter-slide carrier; of a gear-blank carrier supported
for angular adjustment, relatively to the axis of the cutter-slide carrier, and adapted
for oscillatory movement about said axis; and two co-operating actuators
operatively connected together for synchronous movement, and one of which is
operatively connected with, and is adapted for oscillating, the cutter-slide carrier,
and the other of which is operatively connected with, and is adapted for oscillating,
the gear-blank carrier, substantially as described, and for the purpose set forth.
24. In a machine for generating gear-teeth, in combination, a gear-blank carrier,
and a cutter-carrier supported for oscillatory movements about a common center;
a rotative cutter movably carried by the cutter-carrier with its periphery in a plane
radial to the axis of the gear-blank carrier, and adapted for movement toward and
from said common center; means in connection with, and adapted for moving, said
cutter toward and from said common center; and means for oscillating the cutter-
carrier and gear-blank carrier in synchronism, substantially as described, and for
the purpose set forth.
=
25. In a machine of the class specified, in combination, a gear-blank carrier
supported for oscillatory movement about a relatively-fixed axis; a cutter-carrier
supported for oscillatory movement about a relatively-fixed axis;
oscillating said carriers in synchronism and in coinciding directions, and with
means for

page_text: relatively-varying velocities; a pair of rotative cutters supported by the catter-
carrier wit their peripheries in planes radial to a common axis, and operatively
connected for angular adjustment relatively to, and transversely of, each other;
and means for adjusting said cutters relatively to each other, substantially as
described.
26. In a machine for generating gear-teeth, the combination with the oscillatory
gear-blank carrier and oscillatory cutter-carrier; and with actuating mechanism for
imparting comparative movements of relatively-varying velocities to said blank-
carrier and cutter carrier; of adjusting mechanism for effecting a change in the
relative velocities of said blank-carrier and cutter, substantially as described.
27. In a machine of the class specified, in combination, a gear-blank carrier
supported for rotary-reciprocating movements; an actuator in operative connection
with said blank-carrier; a cutter-carrier supported for oscillatory movement about
a relatively-fixed axis; an actuator in operative connection with the cutter-carrier;
a synchronizing connector between, and operatively connecting, the cutter-carrier,
the cutter-carrier actuator and the blank-carrier actuator; a rotative cutter
adapted for movement transversely of the blank-carrier; and actuating mechanism
in operative connection with the cutter-carrier actuator and blank-carrier actuator,
and adapted for rotating the cutter and simultaneously actuating the cutter-carrier
and blank-carrier, substantially as described, and for the purpose set forth.
28. In a machine for generating gear-teeth, in combination, a gear-blank carrier
supported for oscillatory movement; a cutter-carrier embodying an oscillatory
member, supported for oscillatory movement in a path transversely of the axial
line of the blank-carrier; and a cutter-carrier supported by the oscillatory
member for movement transversely of the path of movement of said member;
actuating mechanism connected and adapted for automatically oscillating said
cutter-carrier and blank-carrier in synchronism; a cutter-slide-actuating device
controlled by the oscillatory movement of the cutter-carrier, and adapted for
automatically advancing said cutter-slide, toward and from the axial line of the
cutter-carrier, substantially as described.
29. In a machine for generating gear-teeth, the combination with the gear-blank
carrier, and with means for automatically oscillating said carrier; of an oscillatory
cutter-carrier in operative connection with the gear-blank carrier, and comprising
a cutter-slide-carrying member supported for oscillatory movements transversely of
the axis of the blank-carrier; a radially-disposed cutter-slide supported on said
cutter-alide-carrying member for adjustment in a plane corresponding with the
path of movement of said cutter-slide-carrying member, and also supported for
reciprocatory movement in a plane transversely of the path of movement of said
carrying member; and means for simultaneously oscillating the carrying member,
and advancing the cutter-alide in synchronism with the oscillatory movement of the
blank-carrier, substantially a decribed, and for the purpose set forth.
30. In a machine for generating gear-teeth, in combination, a gear-blank carrier;
a cutter-carrior; means for imparting comparative o cillatory movements to said
blank-carrier and cutter-carrier, synchronously; and adjusting means for changing
the relative velocities of said ear-blank carrier and cutter-carrier, substantially as
described.
31. In a muchine for generating gear-teeth, a blank-carrier, and a cutter-carrier
operatively connected for synchronous rotary-reciprocating movements about axes
radiating from a common center; in combination with mechanism for simultaneously
actuating said carriers; and with means for changing the range of movement of
one carrier relatively to that of the other carrier, substantially as described.
32. In a machine for generating gear-teeth, a gear-blank carrier, and a cutter-
carrier operatively connected together for synchronous rotary-reciprocating
movements about a common center; in combination with actuating mechanism
operatively connecting and simultaneously imparting comparative rotary-recipro-
eating movements of relatively varying velocities to said gear-blank carrier and

page_text: cutter-carrier in synchronism; and adjusting means in connection with said
actuating mechanism, and adapted for effecting a change in the relative velocities
of said gear-blank carrier and cutter-carrier, substantially as described.
33. In a machine for generating gear-teeth, in combination, an oscillatory gear-
blank carrier; an oscillatory cutter-carrier; actuating mechanism in connection
with, and adapted for synchronously imparting comparative oscillatory movements
of relatively-varying velocities to said gear-blank carrier and cutter-carrier; and
an adjusting device in connection with said actuating mechanism, and adapted for
effecting a change in the velocity of one carrier relatively to that of the other
carrier, substantially as described.
34. In a machine for generating gear-teeth, in combination, an oscillatory gear-
blank carrier; an oscillatory cutter-carrier; a gear-blank-carrier actuator; a cutter-
carrier actuator; means in connection with, and adapted for imparting comparative
movements of relatively-varying velocities to, said actuators; and an adjusting
device in connection with said actuators, and adapted for effecting a change in
the relative velocities of said actuators, substantially as described.
35. In a machine for generating gear-teeth, the combination with the oscillatory
blank-carrier and its actuator; and with the oscillatory cutter-carrier and its
actuator; of a shiftable reciprocating connector intermediate to the blank-carrier
actuator and cutter-carrier actuator, and adapted for synchronously actuating the
blank-carrier and the cutter-carrier actuator; and driving mechanism in operative
connection with one of said actuators, substantially as described, and for the
purpose set forth.
36. In a machine of the class specified, the combination with the blank-carrier
and its actuator; of an oscillatory cutter-carrier having a sector at one side
thereof; a reciprocatory rack in mesh with said sector; actuating mechanism for
said rack; and a connector between said rack and the gear-blank carrier actuator,
substantially as described.
37. In a machine of the class specified, the combination with the oscillatory
blank-carrier and its actuator; of an oscillatory cutter-carrier; and a cutter-carrier
actuator operatively connected for synchronous movement with the blank-carrier
actuator, and consisting of a sector carried by the cutter-carrier; a slide supported
for vertical reciprocation, and having a rack in mesh with the sector; a driving-
wheel; and a pitman adjustably connected at one end with the driving-wheel, and
pivotally connected at its opposite end with the rack-slide and adapted for
reciprocating said rack, to impart oscillatory movements to the cutter-carrier and
blank-carrier in synchronism, substantially as described.
38. In a machine of the class specified, in combinatiou, a cutter-carrier supported
for oscillatory movement; a blank-carrier supported for rotary-reciprocating
movements; a cutter-carrier actuator having a vertically-reciprocating member;
a blank-carrier actuator having a horizontally-reciprocating member; a traverse-
bar carried by the reciprocating member of one of said actuators, and having a
sliding-connection with the reciprocating member of the other of said actuators;
and means for reciprocating said traverse-bar, to synchronously actuate the cutter-
carrier and the blank-carrier, substantially as described, and for the purpose set
forth.
39. In a machine of the class specified, the combination with the oscillatory
cutter-carrier and its actuator; and with the rotary-reciprocatory blank-carrier
and its actuator; of a traverse-bar adjustably carried by one of said actuators, and
having a sliding-counection with the other of said actuators; and actuating
mechanism in connection with the traverse-bar carrier, and adapted for
synchronously actuating the cutter-carrier and the blank-carrier, substantially as
described.
40. In a machine of the class specified, the combination with the cutter-carrier
having a reciprocatory member, and with a blank-carrier actuator and its recipro-
catory member; of a traverse-bar pivotally connected, approximately midway of

page_text: its length to one of said reciprocatory members, and having a sliding-connection
with the other of said reciprocatory members; and adjusting means in connection
with said traverse-bar and its carrier, and adapted for effecting a change in the
angular relation of said traverse-bar to said reciprocatory members, substantially as
described.
41. In a machine of the class specified, a cutter-carrier actuator having a
vertically-reciprocating member; and a blank-carrier actuator having a horizontally-
reciprocatory member; in combination with a traverse-bar having sliding-connection
with the horizontally-reciprocatory member, and having a pivotal connection with
the vertically-reciprocatory member; an adjusting device carried by the vertically-
reciprocating member, and in operative connection with the traverse-bar; and an
indicator co-operating with said adjusting device, to indicate the angular position
of the traverse-bar relatively to the horizontally-reciprocating members, sub-
stantially as described.
42. In a machine of the class specified, two independent radius-bars supported
for oscillatory movement, and having concentric axes at the inner ends thereof, and
supported at their outer ends for transverse adjustment relatively to each other;
in combination with two independent cutter-carrying slides supported by the two
radius-bars, respectively, for movement longitudinally of said bar; oscillating
mechanism in operative connection with the radius-bars; and feeding mechanism
in operative connection with, and adapted for simultaneously imparting, a feeding
movement to the two cutter-slides, substantially as described, and for the purpose
set forth.
;
43. In a machine of the class specified, the combination with the two transversely-
adjustable, cutter-slide-carrying radius-bars, and with the cutter-slides carried
thereby of a pair of feed-screws carried by the two radius-bars, respectively,
having screw-threaded bearings in the two cutter-slides, respectively; a telescopic
universal shaft, journaled at opposite ends in bearings upon the two radius-bars,
respectively, and operatively connected with the feed-screws by means of gearing;
and means, substantially as described, for actuating said shaft and feed-screws,
simultaneously, substantially as described.
44. In a machine of the class specified, the combination with the blank-
mechanism frame having a segmental guideway; of a slide supported for adjust-
ment concentric with said guideway, and having transverse blank-carrier-supporting
bearings, and a blank-carrier supported for longitudinal adjustment and rotary
reciprocations in said bearings, and comprising a cylindrical bearing or sleeve
supported for longitudinal adjustment in the bearings of the slide, and carrying
means for adjusting the same transversely of said slide; and a blank-carrying
spindle carried for rotary reciprocations in said cylindrical bearing, and adapted
for longitudinal movement with said bearings, substantially as described.
45. In a machine of the class specific, the combination with the oscillatory
cutter-carrier and its actuator; of a rotary-reciprocating gear-blank carrier
supported for radial and concentric adjustment, relatively to an arbitrarily-fixed
axis; an actuator in operative connection with said blank-carrier, and also in
operative connection with the cutter-carrier actuator; and an index device carried
by said gear-blank carrier, and adapted for indexing the gear-blank, substantially
as described.
46. In a machine of the class specified, the combination with the oscillatory
cutter-carrier and its movable cutter-slide and with the cutter-carrier-actuating
mechanism; of a stopping device controlled by the movements of the cutter-slide,
and adapted for automatically stopping the operation of the actuating mechanism
and cutter-slide, substantially as described.
47. In a machine of the class specified, the combination with the oscillatory and
radially movable cutter-slide; and with the cutter-slide-actuating mechanism
embodying two shiftable clutch-members; of a shifting device in operative
connection with one of said clutch-members, and adapted to be automatically
operated by the radial movement of the cutter-slide, to throw the clutch-members

page_text: out of operative engagement, and stop the movement of the cutter-slide, sub-
stantially as described.
48. In a machine for generating gear-teeth, the combination with the frame-
work; of a segmental cutter-carrier guideway, and a segmental blank-carrier
guideway in rectangular disposition relatively to each other, and their geometrical
axes in substantially the same plane; a cutter-carrier movably supported on the
cutter-carrier guideway; a blank-carrier movably supported on the blank-carrier
guideway; and means for actuating said carriers, substantially as described.
49. In a machine for generating gear-teeth, the combination with the frame-
work having a vertically-disposed segmental guideway; of a segmental gear-
blank carrier slide adjustably supported by said guideway; a rotary-reciprocatory
blank-carrier adjustably carried by said slide; and means in operative connection
with, and adapted for imparting a rotary-reciprocatory movement to the blank-
carrier, substantially as described, and for the purpose set forth.
50. In a machine for generating gear-teeth, the combination with the frame-
work having the segmental blank-carrier-supporting guideway; and with the
rotary-reciprocating blank-carrier; of a pinion carried by said carrier; an
oscillatory segmental rack supported for oscillatory movements; and a pair of
gears intermediate to, and operatively connecting the oscillatory rack and the
pinion upon, the blank-carrier, substantially as described, and for the purpose set
forth.
51. In a machine for generating gear-teeth, the combination with the frame-
work, and with the rotary-reciprocatory blank-carrier; of a segmental rack
pivotally supported for oscillatory movement, in a bearing upon the frame; a train
of gears operatively connecting the blank-carrier and oscillatory rack; and means
in operative connection with, and adapted for oscillating, said rack, substantially
as described.
52. In a machine for generating gear-teeth, the combination with the frame-
work, and with the cutter-carrier and gear-blank carrier; of two oppositely-
disposed sectors, one of which is in operative connection with the cutter-blank
carrier, and the other of which is in operative connection with the gear-blank
carrier, and both of which are operatively connected together for synchronous
movement; and means for synchronously actuating said sector, substantially as
described, and for the purpose set forth.
53. In a machine for generating gear-teeth, the combination with the frame-
work having a segmental guideway; of the blank-carrier slide adjustably carried
by said guideway; a rotary-reciprocatory blank-carrier supported for transverse
adjustment, relatively to said slideway; a driven-gear carried by said carrier; a
driving-gear in mesh with said driven-gear; a bevel-gear carried by the driving-
gear; an oscillatory segmental bevel-gear in mesh with the first-mentioned bevel-
gear; and means, substantially as described, for oscillating said segmental gear,
to impart rotary-reciprocatory movement to the gear-blank carrier, substantially
as described.
HASELTINE, LAKE & Co.,
45 Southampton Buildings, London, W.C.,
Agents for the Applicant.