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Патент USA US2547835

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Apri? 3, 1951
P. A. NEWMAN
2,547,832
MACHINE TOOL
Filed Aug. 29, 1947
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April 3, 1951
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MACHINE TOOL
Filed Aug. 29, 1947
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Filed Aug. 29, 1947
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April 3, 1951
Filed Aug. ‘29, 1947
2,547,832
P. A. "NEWMAN
MACHINE TOOL
7'! Sheets-Sheet 7
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Patented Apr. 3, 1951
2,547,832
UNITED STATES PATENT ()FFICE
2,547,832
MACHINE TOOL
Percy A. Newman, La Fayette, ‘Ind, ,assignor .to
Ross Gear and Tool Company, ‘La Fayette,
Ind, a corporation of Indiana
Application August 29, 1947, Serial No. 1'7 71,249
12 Claims.
1
(01. vv9,0—11.5)
2
This invention relates toamachine-forforming _
‘generally helical cams of :the type employed in
the cam and lever steering gears described in
‘United States Letters Patent Nos. 1,567,997 and
2,071,235, ‘issued respectively to David E. Ross and
.to me.
The Ross cam and lever steering gear em
within a rotating drum and parallel to the drum
axis.
The cutter spindle ‘projects beyond the
'drum at both ends thereof, one projecting end
of the spindle being adapted to receive the cutter
and the other projecting end bearing a pulley belt
connected to an independently mounted cutter
driving motor. To rotate the drum, it is provided
bodies a driven rock shaft having a radially pro
*jecting arm bearing near its outer ‘end a boss
with a gear or gear-sector meshing with a rack
’ which projects parallel to the rock shaft axis and
controlled in position by a movable cam the
is received in a generally helical groove in-a cam 10 ‘contour of which determines the pitch of the cam
operatively connected to ‘the steering Wheel. The
groove at any pointin its length. The cam
theoretical mechanical advantage'of such a steer
moving mechanism is driven from a headstock
ing ‘gear depends upon the ratio between angular
spindle which is directly and positively connected
movement of the scam and angular movement of
‘with the'cam blank, so that the rate of cam move
the rock shaft, and may either ‘vary or be con 15 .ment will'depend .upon the rate at which the head
stant throughout “the range of cam rotation.
stock spindle rotates. To take up lost motion
'It'has previously been proposed, as in my prior
Patent No. 2,234,382, granted ‘March 11,‘ 1941, to
between the headstock spindle and the drum
form a cam for a Ross steering gear by employ
with a second gear or gear-sector meshing with
which ‘supports the cutter, such .drum is provided
ing a cutter corresponding in shape and ‘size to 20 a second rack operatively connected to the ‘piston
the boss of the steering gear and moving such _ of a hydraulic cylinder in which there is main
cutter over a circular arc, corresponding to the
tained a ?uid pressure such that the two racks
path of boss-travel, through the blank as the
exert opposing drum-rotating efforts. ,Power
latter is rotated, the ‘ratio between the rate of
operated means, conveniently hydraulic, is em
blank-rotation and of cutter ‘movement being 25 ployed to move the drum axially of itself and thus
‘controlled to produce a cam of the desired ‘pitch
to move the cutter into and out of association
with the blank. The headstock spindle, and
It is the object of the present invention to im
through it the cam-moving mechanism, is driven
prove the machine of my aforesaid ‘prior patent.
from areversible motor; and such motor, together
‘More speci?cally, it is an object of this invention 30 with valves controlling the hydraulic drum-mov
to produce a cam-cutting machine adapted ‘for
ing means ‘and the tailstock, are automatically
automatic operation and capable of proceeding
controlled by mechanism including switches ac
automatically through a cycle including the steps
tuated by moving parts. The preferred machine
characteristics.
'
of moving the cutter axially of itself into asso
also includes a tailstock clamp which is automat
ciation with the blank, feeding the cutter through 35 ically actuated at the beginning of each cam
the ‘blank as the latter rotates, retracting the
cutter from association with the blank, returning
it to its initial position, and releasing the blank.
Another object of the invention is to provide
an automatic machine in which release of the 40
blank from between headstock and ztailstock cen- ‘
ters prior tothe completion of the cutting ‘opera
tion will be positively prevented.
A further object of the invention is ‘to provide
vcutting operation to lock the tailstock in ad
vanced, blank-supporting position until after the
cutting operation hasheen completed and ‘the
cutter restored to its initial position.
_
The accompanying drawings illustrate a .pre
~terred form ‘of machine embodying my invention:
Fig. l is-a front elevation of the machine, with
parts thereof broken away; Figs. 2 and 3 are
‘elevations, each with parts broken away, illus
an improved means for taking up lost motion or 45 trating respectively the left ‘and right sides‘ of
back-lash between the ‘blank and the cutter?’
the machine; (Fig. 4 is a fragmental view .similar
mounting, ‘whereby to insure uniformity in the
to Fig. :3 showing a modi?ed arrangement of
width of the cam groove and an accurate control
parts; Fig.6 is va plan view of the entire machine;
of its pitch at all points throughout its extent.
Fig. 6 is a plan view, in partial section, of the
Other "objects of the‘invention include the pro 50 ‘work table and associated parts; Fig. I7 is a ver
vision of an'improved means for driving the cutter
tical axial section through the mechanism of
and the provision of cutter-positioning mecha
.‘Fig. 6; Fig. .8 is a vhorizontal section through the
nism adapted for power operation and automatic
upper part-ctthe‘machine; Fig. 9 is a fragmental
control.
.
view similar to Fig. '1 but on an enlarged scale;
In carrying out my invention ‘in its preferred 55 Fig. .10 .(Sheet 1) is a diagrammatic .front eleva
tion of an arrangement of controllingswitches;
form, I "mount ‘the cutter spindle ecc‘entrically
2,647,882
3
Fig. 11 (Sheet 6) is a transverse vertical section
through the tailstock; and Fig. 12 is a diagram
matic illustration of electrical and hydraulic con
nections.
The machine shown in the drawings comprises
4
The shoulder 4| may be the inner case of a ball
bearing through the medium of which the cam
will be supported in the ?nished steering gear.
For the purpose of rotating the headstock
spindle 25 there is secured to it (Fig. '7) a worm
a hollow base l5 from which there projects up
wardly a column l6 carrying a housing I'I. With
in the housing IT a drum I8 is mounted for rota
tion about a vertical axis as well as for vertical
gear 45 meshing with a worm 46 which is oper
move over an arcuate path when the drum [8 is
in the cam blank 21 will depend upon the rela
atively connected through gears 41 and 48 with
a countershaft 49.
The countershaft 49 extends
outwardly from the headstock 23 (Fig. 6) and
sliding movement. Within the drum 18, there is 10 is there provided with a pulley 50 connected by
a belt or belts 5| with a pulley 52 on the shaft
rotatably mounted a cutter-spindle [9, the axis of
of'a driving motor 53. In the preferred ma
which is parallel but eccentric to the axis of the
chine, the motor 53 is a reversible hydraulic mo
drum. The lower end of the cutter spindle l9
tor; but other types of motors may be used if
projects downwardly beyond the drum and is
there equipped for the reception of a milling 15 desired.
As will be obvious from the contruction so far
cutter 26. Because of the eccentric position of
described, the conformation of the groove cut
the spindle [9 in the drum l8, the cutter 26 will
tion between the respective speeds of rotation of
' the cutter-spindle [9 corresponds to the center 20 the headstock spindle 25 and the drum l8. To
control such relative speeds, the drum I8 and
line distance between the driven rock shaft and
the spindle 25 are operatively interconnected
, the cam-engaging boss in the steering gear above
referred to, and the shape and size of the cutter’. through the medium of a rectilinearly slidable
rotated in the housing H. The eccentricity of
cam carried on a cam-slide 55 (Fig. 1) which is
For the purpose of supporting a cam blank in 25 moved longitudinally of itself at a rate depend
ent upon the speed of rotation of the spindle 25
, co-operative relation with the cutter 20, a work
h 20 corresponds to the size and shape of such boss. '
and which, through an appropriate cam fol
lower and other mechanism to be hereinafter
described, controls the speed of rotation of the
‘which respectively support aligned spindles 25'
and 26 between the opposed ends of which a cam 30 drum l8. The mechanism for moving the cam
slide 55 longitudinally of itself comprises a verti
block 21 is adapted to be supported. The com
cally movable rack 56 which is operatively con
' mon axis of the spindles 25 and 26 is horizon
nected to the cam-slide 55 through the medium
‘ tal—i. e., it lies in a plane normal to the axis.
of a bolt 5'! and turnbuckle 58 (see also Fig. 3).
' of the drum |8-and the work table 22 is so 10-“
'_‘cated that the distance between the spindle axis 35 The rack 56 is supported for vertical sliding
movement in a housing 60 which, for a purpose
and the axis of the drum l8 corresponds to the
to become apparent hereafter, is in turn verti
distance between the receptive axes of the cam
cally movable in ways 6! supported from the base
‘ and rock shaft in the steering gear.
[5. For the purpose of moving the rack 56 verti
The particular cam-blank shown in the draw--v ‘
' ing comprises (Fig. 9) a central cylindrical body 40 cally, it meshes with a pinion 63 which is ?xed
on a shaft 64 rotatably mounted in the hous
portion, in which the cam-groove is to be cut,
table 22 supported on the base 15 is formed to
provide a head-stock 23 and a tail-stock 24 .
and reduced-diameter end portions 30 through
' which the cam may be rotatably supported in 4
ing 60.
Exteriorly of the housing 60, the shaft 64
carries a driving gear 65 which is adapted for
the housing of the ?nished steering gear. In
addition, the cam-blank is provided at its op 45 operative connection with a pinion 66 ?xed to
the rear end of the headstock spindle 25. The
posite ends with centers by which it may be
,_ located laterally, of itself to be concentric with
the spindles 25 and 26.
As shown, the centers
Y are male centers 3| and 32 formed by imparting '
a conical shape to the outer ends of the journals 50
I 30; but it is to be understood that female centers
Y ‘may be used if desired. The cylindrical body
portion of the cam is provided at one end with a
notch or groove 33 to facilitate positive rotation “
of the cam-blank during the cutting of the cam 55
groove.
gear 55 may, as indicated in Figs. 3 and '7, mesh
directly with the gear 66 or, if it is desired to
reverse the relation between the direction of ro
tation of the headstock spindle 25 and the di
rection of movement of the cam-slide 55, the
gear 66 may, as indicated in Fig. ll, mesh with
an idler 61 rotatably supported from the hous
ing 60, such idler in turn meshing with the gear
66 on the headstock spindle. By changing the
relative sizes of the gears 65 and 66, the ratio
between the speed of movement of the cam-slide
Within the tail-stock spindle 26, which does
55 and the speed of rotation of the spindle 25
_> not itself rotate, I provide a rotating center 35
formed at its outer end to receive the center 3! ‘ can be varied.
It is to make possible the use of different-sized
The rotatable head —stocl~.'
' of the cam-blank.
gears 65 and ‘66 that the housing 60 is made
‘spindle 25 is provided with an axially slidable
vertically adjustable in the ways 6|. Any con
center 36 which, like the tail-stock center 35, is
venient means may be employed for locating the
. provided at its outer end with an axial opening
housing 6|] in the proper vertical position, the
adapted to receive the blank-center 32. The ’
headstock center 36 is urged forwardly by a 65 means indicated in the drawing (Fig. 3) com
prising a nut 10 which is secured in the housing
_ spring 31, movement of the center under the in
'
6|] and which receives a vertical lead screw ‘H
?uence of the spring being limited by a bolt 38.
rotatably mounted in the base I5. The lead
‘For the purpose of transmitting toroue from the
screw ‘H may be connected through gearing 12
‘ headstock spindle 25 to the cam blank 21, an‘
adapter 46 is secured to the end of the spindle. 70 with an adjusting shaft 13 which projects
. Such adapter is formed to engage a shoulder 4|
on the cam blank to locate the latter axially of
itself with reference to the axis of the drum [8.
- through the wall of the base I5 and is there pro—
vided with a hand wheel 14 (Figs. 1 and 6).
The cam-slide 55 previously referred to is sup
ported for vertical sliding movement in suitable
In addition, the adapter is provided with a key
42 received in the notch 33. in the cam body. 7.5 guides 16 (Figs. 1 and 8) mounted on the op
:; 2,11
6
'~ ipnsite side of ‘the'houslng "I1 ‘.from the drum l8.
'1 interconnection of the link :H'EI with the vspindle
" ‘iIhe cam slide, “in the preferred arrangement, is
. 19 and bracket 1 08 coincide respectively with the
:"provided centrally with a swivel 11 upon ‘which
95a compensating plate 718 is carried for angular
"adjustment. ‘To control the angular position of 6
~axis of the spindle and the axis of the pulley
' Mil.
The link 410 may be made ofv adjustable
length ‘to control the tightness of the ‘belt 105..‘
ltis desirable in most instances to provide for
vertical movement of the drum l8 and of the cut
ter :and cutter~spindle supported therefrom, vTo
accommodate for such vertical drumemovement,
’ vthe compensator plate 118 with reference to the
cam-slide 55, ‘it is provided with ‘an outwardly
. projecting lug 19 received between two ‘set screws
/ ‘.80 ‘mounted in bosses BI on the slide 55. ‘To 10
cate the compensator plate de?nitely in any po .10 ‘the drum ‘may be provided with an upwardly ex
":sition of adjustment, it :is provided with arou
tending spindle-housing H2 (Fig. l.) which sur
.:atc slots 282 which receive clamp screws .83 ‘ex
rounds and :isconcentric with the spindle I9 and
- .tcnding :into the cam slide.
‘wh‘iohisrotatably and slidably received in the ad
' ~' :Upon the compensator plate 18 there are '10-“
jacent :end of the link H6. The link I ll] has an
cated in fixed positions a pair of cam segments:v 715 integral extension I I3 .(Fig. v5) provided with an
185 and 86 ‘having opposed surfaces which de?ne
opening H4; and .a boss H5 projecting upwardly
between them a cam groove 88 extend-ingobliqu?
from the top of the column t6 carries a retainer
~-.:ly of the path of ‘travel of the cam slide 55. Such Y
“6 which overlies the link-extension H3. With
- groove receives a cam~iollowing roller 98 rotate
‘such an arrangement, the link I I0 is con?ned to
ably mounted on a slide 91 supported for hor1-" :20 movement in a single horizontal plane by-the top
aontal sliding movement from the housing 11.
of the column and the retainer H5, and hence
~ “The slide 91 is rigidly connected, as by means of
a bolt 92, with a rack 93 which meshes with a
does not bind :on the spindle-housing I I2 as the
‘drum 18 :moves vertically.‘ The opening H4 is of
gear or gear-sector 94 rigid with the drum I8. . course :made sufficiently larger than the boss I I 5
.As the headstock spindle 25 rotates it causes 25 to prevent interference with movement of the link
- the cam slide .55 to move vertically at a speed
in its plane as the drum -I 8 rotates.
bearing a de?nite ratio to the speed of spindle .. ‘ As has ‘been noted above, thedrum I8 is axially
_ rotation; and as the cam-slide :55 moves yerti- ‘
slidable .as well as rotatable in the housing ll.
. cally, the cam follower 9!] in the oblique groove
This permits the cutter 28 to be positioned
"30
88 moves horizontally at a controlled irate totmoye
‘properly with reference ‘to the blank-axis dur
the rack '93 and cause thedrum 1.8 to swing about
its axis. Obviously, the ratio between the rate
. of movement of the cam-slide 55 and the rate .of
angularjmovement of the drum 18 about its ‘axis’
_.will depend upon the obliquity ‘of the groove 88.1
‘ To remove alllost-imotioncr backlash and vthus "
,,_to insure that arcuate movement of the cutter ‘29 . about the .axis of the drum J8 will proceedat- a
de?nite rate determined by ‘the obliquity of ‘the
Y groove 88, I apply to the drum It a ‘load which‘
opposes the effort exerted by the cam 85-435 on
the cam follower. To this end, the drum I8 is pro—
140
vided with a second gear or gear-sector I00v which .
ing the cutting operation and also permits the
cutter to 'be elevated above the blank to provide
greater clearance during ‘removal and insertion
‘of blanks.
“To accommodate for axial movement of the
drum 1E8 the pulley I95 has .a face-width great
enough to enable it to remain in cooperative .re
lation with the belts IE5, and the gear sectors 94
and H30 have face widths great enough to enable
them to ~remain in meshing engagement with the
respectively associated'racks ~93 and .10 I. During
the cutting operation, the vertical disposition
of the cutter 20 maybe controlled by a cam or
meshes with a rack IllI operatively connected to a
piston I02 (Fig. 5:) in a hydraulic cylinder I103? i345 cam-segment 120 which is secured to the lower
end of the drum l6 :and which rests on a roller
{I21 mounted on an axis radial of thedrum. The
roller I24 is supported on the upper end of a mem
‘ With this arrangement, two methods of opera
tion are possible depending upon which ‘end of
, the cylinder N13 is connected to a source of fluid
ber 122 which is mounted for vertical sliding
pressure during the cutting operation. In other
words, the hydraulic mechanism can ~be operated $50 :moylement ‘in a housing I23 secured to the base
I5. ‘In ‘its ‘lower end, the member I22 is provided
either to effect or to oppose feed of the rotating
with a screw-threaded axial opening receiving a
lead screw 122’ connected, as through gearing
"1:24, with an :adiusti-ng wheel or crank I 26.
' cutter 20 through the‘blank 2i. In'the former in
stance, the actual cutting effort is obtained from
the hydraulic mechanism, ‘and the rate of feed
‘ is controlled by the rate of vertical movement
of the cam slide ‘55. “In the other instance, the
‘hydraulic mechanism opposes feed of the,’ cutter
I
As will be obvious, with the spindle I18 urged
downwardly by means hereinafter described to
' hold the cam 12!] in contact with the roller IZI,
the vertical elevation of the cutter 2.0 during
the cutting operation will depend upon the con
anism which operatively connects ‘the headstock, 'iBI) tour of the cam J20. By adjusting the wheel
‘SpindlefZE Widths drum I8. thusinsuring that an 1 4-26, the roller 121 may be raised or lowered .as
desired to establish-for the spindle .a base ele
“lost-motion “in such ‘mechanism will ‘be taken up vation departures from which are controlled by
‘throughout the cam-cutting operation.
: ‘
.
through the cam blank to insure the imposition
~ of a predetermined minimum ‘load on themec'h
the cam. Change of elevation of the cutter 20
For the purpose of rotating the cutter spindle
I9 it projects ‘beyond the upper end of the drum‘ 165 during the cutting operation will ordinarily be
relatively slight, as its chief purpose is to ac
[8 and the housing H, where his provided with a
commodate the cam to compensate for wear.
"pulley I85 connected by a belt or :belts .t?? "to a
pdrivegpulley It}? on the shaft of .a spindle-driv
To move the spindle l8 vertically to offset .en—
easement and disengagement of the cam ‘.820
' "ing' motor 1.08. ‘To accorrunodateifor thearcuate
8
with the roller 121., it is'provided with anannular
rotates during the cam-cutting operation, “the
:groove Hill which receives a block .l3I ipivotally
motor I03 "is‘mounted {on a bracket 109 whichis
mounted .on one ‘arm of :a bell crank I32. The
? swingably supported on a ‘vertical axis from the
other end of the bell crank is operatively :con—
'nected with a piston 1.33 which is slidable in a
. movement of the cutter spindle .I 9 asthe
top of the column 16 and which is econnectedby a
“slink 1 MI with'the spindle i9. The-axes or ‘pivotal
75
cylinder 134. i'Referring ‘to Fig. :1, ‘it will be :ob
' 2,547,832
7
vious that upon the application of ?uid pressure
to the left-hand end of the cylinder I34, the
piston I33 will be moved to the right to swing the
bell crank I32 and elevate the spindle I8, thus
freeing the cutter I9 from engagement with the
blank and/or providing more room for removal
and insertion of the blank. Conversely, the ap
8
26, in raising and lowering the drum I8, in ac
tuation of the rack IOI , and in operating the mo
tor 53, I may employ a pump I56 adapted to be
driven by an electric motor I51. Conveniently,
the pump I56 is located in a sump I58 associated
with the base I5 of the machine and is arranged
to draw liquid from such sump and to discharge
it, under the control of valves to be described
hereinafter, to the various hydraulically oper-,
the left to lower the spindle I8 and force the cam 10 ated devices.
In Fig. 12 I have illustrated diagrammatically
I20 into engagement with the roller I2I.
one arrangement of electrical and hydraulic con
Like vertical movement of the drum I8, ad
nections by which completely automatic con
vance and retraction of the tailstock spindle 26
trol of the cam-cutting machine may be effected.
may be accomplished by hydraulic means. To
this end, the tailstock spindle 26 (Fig. 7) is op 15 As there indicated, the pump I56 withdraws liq
uid from the sump I 58 through a pipe I60 and
eratively connected with a piston I36 slidable in
discharges such liquid under pressure into a pipe
a cylinder I31 to either end of which ?uid pres
I6I. The pipe I6I has associated with it a pres
sure can be applied by appropriate valve means.
sure-relief valve I62 discharging into the sump
Automatic or semi-automatic control of the
machine may be provided in response to the 20 I50. The pipe I61, containing liquid under pres
sure, is adapted to be connected by appropriate
movement of various parts. Conveniently, such
valve mechanism with the various hydraulically
automatic or semi-automatic control is exercised
operated devices ?uid from which ?ows through
through the means of limit switches, three of
plication of ?uid pressure to the right-hand end
of the cylinder I34 will move the piston I33 to
a return pipe I63 to the sump I58.
which are shown in Fig. 1. The switches there
.25
Hydraulic operation of the tailstock spindle 26
shown comprise a switch I40, actuated by the
is controlled by a valve I66 having a movable
mechanism which moves the drum I8 vertically,
and two switches HI and I42 which are con
trolled in response to movements of the rack 93.
Means for operating the switches MI and I42 30
may comprise a switch actuator I43 operatively
connected (Fig. 8) with the rack 93 as by being
attached to the outer end of an arm I44 project
ing forwardly from the rack 93. Mechanism for
operating the switch I40 may comprise a pivoted 35
lever I45, the rear end of which is operatively
connected with the piston I33 and the front end
of which co-operates with the switch I40.
For fully automatic operation of the machine,
valve member I61 which can be moved alteratively
to connect either end of the cylinder I31 to the
?uid supply line I6I and simultaneously to con
nect the other end of the cylinder to the return
line I63. In the particular arrangement illus
trated in Fig. 12, the valve member I61 is mov
able under the control of a hand lever I68 and a
solenoid I69, the solenoid operating when ener
gized to connect the right-hand end of the cylin
der I31 to the ?uid-supply line I6I.
_
A similar valve I1I having a movable valve
member I12 is employed to control the supply of
?uid to the cylinder I34 and thus to control ver—
'tical movement of the drum I 8. Movement of the
valve member I12 is controlled by two solenoids
I13 and I14, the former operating when ener
gized to position the valve member I12 to con
nect the left-hand end of the cylinder ! 34 to the
?uid-supply line I6I and the latter operating
when energized to connect the right-hand end of
I may employ a third switch, indicated at I41 40
in Fig. 10, controlled by movement of the rack
93. As will be apparent from Fig. 10, the switches
MI and I42 are controlled respectively by bosses
I48 and I49 on the actuator I43, while the switch
I4‘! is controlled by a dog I50 movably mount 45
ed on the actuator I 43. It is assumed in Fig. 10
that during the cutting of the cam the rack 93
the cylinder I 34 to such ?uid-supply line.
will move from right to left, and the dog I50
A third valve I16, similar to the valves I66 and
on the actuator I43 is arranged to override the
switch I41 without operating it during such for 50 HI and embodying a movable valve member I11,
controls the supply of ?uid under pressure to the
ward feeding movement of the rack 93 but to
reversible hydraulic motor 53. That motor has
actuate the switch I41 during the return stroke
two ports, which are connected respectively to two
of the rack. The manner in which the switches
ports of the valve I11 by conduits I 18 and I19,
I4I, I42, and I41, as well as the switch I40, con
trol the various operations in the machine will 55 and is so constructed as to rotate in one direction
when fluid under pressure is supplied to it through
be brought out hereinafter.
the conduit I18 and in the opposite direction when
If desired, the tailstock 24 may be provided
it receives ?uid under pressure from the conduit
with means for locking the tailstock spindle 26
I19. The valve member I 11 is biased, as by op
in advanced position to insure against accidental
retraction of the tailstock spindle and dropping 60 posed springs I80, toward a neutral position in
which neither of the conduits I18 and I 19 is con
of the blank 21 during the cutting operation. One
nected to the ?uid supply line I63 and is adapted
suitable form of spindle-clamping means is il
to be moved in opposite directions from such neu
lustrated in Fig. 11, where I have shown the tail
tral position by two solenoids IOI and I82. The
stock 24 as provided with a clamping member
I52 mounted for sliding movement generally tan 65 arrangement is such that when the solenoid I8I
is energized the valve member I 11 is moved to
gentially of the tailstock spindle 26 and provided
connect the conduit I18 to the supply line I63
with a spindle-engaging surface I53. The clamp
and the conduit I19 to the return line I 63. Con
ing member I52 may project laterally from the
versely, when the solenoid I82 is energized, .the
tailstock 24 into association with a solenoid I54
which, when energized, will operate to force 70 valve member I11 is moved in the other direction
into a position in which the conduit I19 is con
the spindle-clamping surface I53 against the
spindle 2'6 and prevent its‘longitudinal move
nected to the supply line I6I and the conduit I18
to the return line I63. When neither solenoid
ment.
is energized, the springs I80 hold the valve mem
As a source of fluid under pressure for use in
ber I11 in its neutral position. For the purpose
advancing and retracting the tailstock spindle
auassa
9;
‘l0 .
of explaining operation, it is assumed that ener
I
open when the other is closed. The switch I41...
gization of the solenoid I8I to connect the conduit
I18‘ with the supply line I6I will result in forward
which is also operated in movement of the rack
93 as above set forth, is a normally open, single-..
rotation of the motor 53, or rotation in the direc
pole switch adapted to be closed momentarily
tion employed in the cam-cutting. operation. To
near the end of the cutter-return stroke of the
rack 93. The switch I46, operated by the mech_-_v
control the speed of the motor during the cam
cutting operation, the conduit. I18. may embody
anism which raises and lowers the drum I8 is
a single-pole switch normally open when the
drum I8 is. raised but closed when such drum
its reverse rotation, a bypass including a check 10, is lowered.
valve I 84 is provided around such valve.
The solenoid I69 which operates when ener
The lost-motion take-up mechanism embody-v
gized to move. the valve member I61 to, retract
ing the rack IOI, piston I02, and cylinder I93,
the tailstock spindle 26 is controlled by a relay‘
which imposes on the drum I8 a load opposing
29I. ‘The winding of the relay 21H is connected
a ?ow-regulating valve I83, and to prevent such
valve from reducing speed of the motor 53 during
its rotation during the cam-cutting operation,
, across the conductors I9I. and I92 in series with
the normally open switch M1.
may conveniently be controlled jointly with the
motor 53. For this purpose, and as indicated in.
The solenoid I54, which operates when ener
gized to lock the tailstock spindle against longi
Fig. 12, the left-hand end of, the cylinder I93 is»
connected to the conduit I18 and the right-hand
tudinal movement, is controlled by‘a relay 292,.
20v the winding of which is, connected across the‘v
end to the conduit I19.
- The spindle-driving motor I03, the pump-driv
ing motor I51, and the various solenoids above
conductors I9I and I92 through the contacts 12
of limit switch I42.
The solenoid I14, which positions the valve.
mentioned are arranged to. be controlled by in
member I12 to, cause lowering of the drum I8,
dividual relays. Desirably, the motors. and sole
noids are adapted to be operated by some readily 25 is controlled by a relay 263 whose winding is
connected to the conductors I9! and. I92 through
available current, such as the common 119 volt,
a normally open. cycle-start switch 2B4. The
60-cycle alternating current, while the various
control relays are low-:voltage relays operating
solenoid I 73., which Positions the valve member
on current derived from a step-down transformer
il2 to cause raising of the drum I8, is. controlled
I99 over conductors I9I and I92.
One of such 30 by the contacts a of a relay 205 which also ern.
conductors I9I and I92hoii1nofbersrpwaETAOI
conductors, shown as the conductor I9 5, desirably
includes a normally closed, master stop switch
I93 which can be manually opened at any time to
de-energize all the control relays and stop oper~ 35
ation of the machine.
' The supply current to the spindle-driving mo~
bodies a set of. holding contacts b. The winding
of relay 265. is. connected through the. contacts
a of limit switch I4I to the conductors I9I and
I92.
The remaining relays 296 and 261 respectively
control solenoids IBI and I82 which, in turn,
control operation of the motor 53, and the baclse
lash takeeup mechanism IIlI—IIJ3. Each of
tor I98 is controlled by a relay I95 having con
those relays comprises pairs of contacts a con.
tacts a in circuit with the motor I98, and two
pairs of holding contacts I) and c. The winding 4.0 trolling the. associated solenoid. and a pail‘ of
auxiliary contacts I).
.
of the relay I95 is connected across the relay
supply conductors I9I and I92 through a nor- '
mally open, manually closable switch I96 with
which the holding contacts 0 of‘ the relay are in
parallel. ‘Upon a momentary closing of the switch
I96, the relay I95 is energized to close all its
contacts. Closing of the contacts a results in
supply of current to the spindle-driving motor
The winding of the relay 295 is ‘included- in a
circuit
extending
from
the . conductor
I9I,
through the contacts b of limit switch I4I, the
relay winding, the switch I46, and the contacts
a of limit switch I42 to the conductor I92. The
contacts b- of relay 296, when closed, provide
connection of the winding of that relay to the
I08, while closing of the contacts 6' completes a 50. conductor I92 irrespective of the condition of
switch I46 and contacts a of switch I42. The
holding circuit including the winding of the re
lay I95 and thus maintains such relay energized
until the master stop switch I93 is opened. Clos
ing of the contacts b is without e?ect on the relay
I95, but does perform a function to be herein 55
after ‘set forth.
,
The pump-driving motor I5‘? is controlled by
a. relay I98 having contacts a controlling the
supply of current to the motor I51 and a pair of
holding contacts b. 'The relay-winding I99 is
connected across the‘c‘onductors I9I" and I92 in
winding of relay 20‘! is connected in a circuit
extending from the conductor I9I through the
contacts b of limit switch I42, the relay winding,
and the contacts b of relay 295 to the conductor
I92. The contacts. b of. relay 2!" are in parallel
with the contacts b of relay 295.
Operation
, Figs. 1, 2, and ‘8 illustrate the drum It as 10w
ered, the racks 93 and I9I as at the midpoints
of‘their respective range of movement, and the
‘series with both a normally open, manually clos
cutter 2n and cutter-spindle'le as at the mid
able switch I99 and with the contacts b of relay
point of their are of travel. It will be under»
I95, while the contacts b of relay I98 are con
stood, however, that at the beginning of a came
nected in parallel with the switch I99. As a result 65 cutting operation, the cutter 253 will be at one
of the fact that the winding of relay I99 is con~
end of its arc of travel. '
nected to the conductors I9I and I92 through the
The parts of the machine illustrated in Fig. 12
contacts b of the relay I95, the relay I93 can be
are shown in the position existing. at. the start
energized to cause operation of the pump-driving
of a cycle. As previously indicated, it is assumed
motor I51 only when the relay I95 is closed to 70 that. the drum-rotating rack 99 will move to the
cause operation of the spindle-driving motor I98.
left during the cam-cutting operation, and'such
; The two switches MI and I42, which are op
rack will therefore be, at the right-hand limit of
erated in movement of the rack 93., are both
its travel with the boss I 49 of the. switch actuator
double-pole, double-throw switches each having
plate I43 in engagement with the switch I42 to
two sets of contacts a and b vone oi which, is 75 hold the contacts a thereof closed and the con
ablrifs'sé
12
As the cam slide 55 moves vertically, the cam"
follower 90 traverses the oblique groove 88 thus,
under the assumed conditions, causing leftward
tacts b thereof open in opposition to an appro
priate biasing means incorporated in such switch.
The other switch-actuating boss I48 will be dis
posed out of engagement and to the right of the
limit switch MI, and an appropriate ‘biasing
movement of the rack 93 and clockwise (Fig. 8)
rotation of the drum I8. During this movement
of the drum, the cutter 20 swings in a circular
arc; and as the blank 21 is being simultaneously
rotated, the cutter forms in the blank a generally’
means associated with such switch will maintain
the contacts (1 thereof open and the contacts b
closed. At the beginning of the cycle, the drum
I8 will be in its upper position to elevate the cut
ter and facilitate insertion of a cam blank 21, 10
and the piston I33 in the cylinder I34 will be
near the right-hand end of such cylinder, being
held there by ?uid pressure applied to the left-_
hand end of the cylinder under the control of
helical groove 21’ such as is shown in Fig. 9.‘
As the rack 93 moves to the left from the posi
tion it occupies at the start of the cycle, the
switch-actuator boss I49 moves out of engage
ment with the limit switch I42 to open the con
tacts a and close the contacts 1) thereof. Opening
of the contacts a of switch I42 is without any im
mediate effect on the relay 206; as such relay
the valve I1I which was set in the position to
accomplish that end by energization of the sole
remains energized by reason of the engagement
of its contacts b in the holding circuit. Accord
ingly, the solenoid I8I remains energized and
plied to the right-hand end of the cylinder I31
under the control of the valve I66. Energiza 20' the motor 53 continues to operate in the for
ward direction. Closing of the contacts I) of
tion of the solenoid I69 during the preceding
switch I42 completes a circuit from the con
cycle has resulted in a setting of the valve I66
ductor I9I, through such contacts and the wind
which provides for the application of ?uid pres
ing of relay 202 to the conductor I92. Energiza
sure to the right-hand end of the cylinder I31.
All the relays 20I, 202, 203, 205, 206, and 201 25 tion of the relay 202 causes current from the sup
ply line to be supplied to the solenoid I54 which
will be open.
operates to engage the tailstock clamp I52 to
To begin a cycle, the operator places a blank
prevent any accidental release of the tailstock
21 between the headstock and tailstock spindles
noid I13 during the preceding cycle. The tail
stock 26 will be retracted by ?uid pressure ap
spindle.
and operates the lever I68 to move the valve
When swinging movement of the cutter 20 has
member I61 of the valve I66 to the left. When 30
progressed far enough to complete the cutting of
this occurs, ?uid pressure is applied to the left
the groove in the cam blank, the boss I48 on the
hand end of the cylinder I31 to advance the
actuator I43 engages the switch I4I to close the
tailstock 26 and clamp the blank between the
contacts a thereof and open the contacts b there
centers 35 and 36. Assuming that the spindle
driving motor I08 and the pump-driving motor 35 of. As the contacts b are in series with the wind
ing of relay 206, such relay is immediately de
I51 have been started by successive momentary
energized to de-energize the solenoid I8I of the
closings of the switches I96 and I99, the operator
motor-control valve I16. The closing of contacts
now closes the cycle-start switch 204 to energize
a of switch I4I causes energization of the relay
the relay 203 and thereby cause current to be
205, and the resultant closing of contacts a of
supplied to the solenoid I14. Upon energization
such relay energizes the solenoid I13 causing it
of such solenoid, the valve member I12 is drawn
to operate the valve I1I so that ?uid under pres
to the right to connect the right-hand end of the
sure will be supplied to the left-hand end of'the
cylinder I34 to the ?uid supply line I6I and the
cylinder I34. The ?uid supplied to the cylinder
left-hand end of such cylinder to the return line
I63. As a result, the piston I33 will be moved 45 I34 moves the piston I33 therein to the right,
thus causing the drum I8 to be elevated. Upon
to the left in the cylinder I34 to swing the bell
this upward movement of the drum I8, the switch
crank I32 in a counter-clockwise direction, and
I40 is restored to its normally open position; but
thus, in the manner previously brought out, to
no action occurs as the result of such switch
lower the drum I8 until the cam I20 engages the
roller I2I which determines the vertical position 50 opening as the circuit through the switch was
previously broken by the opening of contacts
of the cutter 20. In this leftward movement of
I42a at the beginning of the cycle.
the piston I33, the lever I45 (Fig. 8) operates to
'
Simultaneously with the closing of the con
tacts Ia of relay 205 to cause elevation of the drum
I8, the contacts b of such relay close to complete
a circuit from the conductor I9I through the
closed contacts I 42b, the winding of relay 201,
closing of the auxiliary contacts I) of relay 206
and the contacts 20% to the conductor I92. This
completes a holding circuit which is in parallel
causes energization of the relay 201, whose con
with the series-connected switch I40 and con
tacts I4>2a but which includes contacts b of limit 60 tacts a close to energize the solenoid I82, which
operates the valve I16 to reverse the ?ow of ?uid
switch I4I. Energization of the solenoid I8I
through the motor 53. The concurrent closing of
causes the valve member I11 to move to the left
the relay contacts 201b completes a holding cir
from its neutral position, thus connecting the
conduit I18 to the ?uid supply line I6I‘ and the , cuit which includes the winding of relay 201 and
conduit I19 to the return line I63. The resultant 65 the contacts b of limit switch I42.
The reversed rotation of the motor 53 moves
?ow of ?uid through the motor 53 under control
the cam slide 55 to cause the rack 93 to move to
of the valve I83 causes the motor to operate to
the right, thus rotating the drum I8 to restore
drive the headstock spindle 40 and, through it, the
the cutter to its initial position. As the rack 93
mechanism which produces vertical movement of
the cam slide 55. Simultaneously, pressure is ap 70 begins its rightward movement, the switch
actuator boss I48 moves out of engagement with
plied to the left-hand end of the cylinder I03 to
the limit switch I4I to open the contacts a and
oppose the leftward movement of the rack IOI
close the contacts b thereof. The change in the
which accompanies leftward drum-rotating move
close the switch I40. As both the contacts I4Ib
and I42a are already closed, closing of theswitch
I40 energizes relay 206 to cause current to be
supplied to the solenoid I8I. The concurrent
__ment of the drum-driving rack 93 under the con
trol of the cam 85-86.
73
condition of neither of these contacts has any
immediate effect on the movement of machine
gasses
14'
elements. Although opening of'the contacts M‘Id I
tov insure the existence of sufficient-pressure ini "
does de-energize the relay 2%,, interrupt the sup
the cylinder I03 to force the cutter through the.
blank during the cutting operation. In the ?rst
case, with the cam-groove 88‘ having the‘ obliquity
indicated in Fig. l and with the racks ill and IUI
moving‘ to the left during the cutting operation,
ply of.‘ current to the solenoid I13, and open the
contacts 20%, the valve member I12‘ remains in
the position ‘to which. it was moved when the
solenoid [1.3 was initially energized and the re— ’
lay 20'! remains energized because its‘ winding is '
the reaction of the blank on the cutter and the
included in the holding circuit: through contacts
pressure in the left-hand end of the cylinder I03
20‘Ib and limb. The closing of contacts I4I'b is
both serve to hold the cam-follower 90 in contact
without effect, as the, circuit including the con~ 10 with the cam-segment 86; and‘ the latter, as it
tacts and winding of relay‘ 206 was already open.
rises, rotates the drum I8, forces the cutter
In. consequence, the solenoid‘ I82 remains ener
gized and the motor 53' continues to operate in
through the work, and causes ?uid under pres
sure to be expelled from the cylinder I 03‘. In the
the reverse direction to move the rack 93 to the '
second case, under the same assumed conditions,
right. As rightward‘ movement of the rack 93 15 fluid-pressure in the right-hand end of cylinder
nears completion, the dog I50‘ on the switch
I03 rotates the drum in the clockwise direction,
a'ctuator I43 momentarily closes the switch It‘!
urges the rack 9| to the left, and holds the cam '
to energize the relay MI and cause current to be
fol-lower 90 in contact with the cam-segment 85;
supplied to the solenoid I69. Such solenoid‘ op
' and the latter,.as it rises, merely controls the rate
crates‘, when energized, to reverse the valve I66 20 at which the drum rotates under the e?ort ap
and supply ?uid under pressure to the right-hand
plied to it‘ by the rack IOI. In both cases all
end of the cylinder I31. The pressure thus ap
lost motion between the drum and headstock
plied to the piston I33 urges the tailstock spindle
spindle is taken up.
26 in the direction of retraction; but as the clamp '
Fig. 12 is intended to represent one arrange
I152 is still engaged, the tailstock remains ad 25 ment of connection and control apparatus
vanced.
through which automatic operation of the ma
Upon completion of the return movement of ‘Y
chine may be accomplished. O-ther arrange
the rack 93, the projection I ail-on» the switch
ments are possible; and in most instances it will‘
actuator I43 re-engages the limit switch Hi2 tov
be desirable to include in the apparatus switch
close the contacts a and open the contacts 2')
mechanisms by which control of movements of
thereof. Closing of the contacts a is without im
individual parts may be exercised in order to
mediate effect as the circuit containing them has
iacllitate setting up the machine.
already been opened; but opening of the contacts
' The effective pitch of the cam cut‘ by the ma—
I42 opens the circuits‘ through both the relays
chine will depend upon the shape of the cam
202 and 201, thus causing de-energization of the 35 groove 88', the setting of the compensator plate
clamp-actuating solenoid I54‘ and of the valve
‘I8, and the ratio of the gearing interconnecting
controlling solenoid ISZ. When the clamp-actu
theheadstock spindle with the cam-slide 55. If
ating solenoid £54 is de-energized, the clamp I52
the cam-groove 38 is straight, the effective pitch
is released; and ?uid pressure in the right-hand
of the cam will be uniform throughout the ex
end of the cylinder I31 retracts the tailstock 26. 40 tent of the cam; but by employing cam-segments
De-energization of the valve-controlling solenoid
85 and 86 which will provide a groove having
I82 frees the valve member IT! for movement
differently inclined portions, a cam of non-uni
form pitch can be produced. A steering gear
under the in?uence of‘ the springs‘ I83, which
operate to restore such valve member to its neu
embodying such a cam is disclosed in my prior
tral position in which supply of ?uid to the motor
Patent No. 2,071,235. Fine adjustments to e?ect
53 is shut oil“, thus bringing. the headstock. spindle
small changes in cam-pitch may be secured by
and the cam slide 55 to rest.
changing the angular position of the compensator
When the machine operates in the manner
plate ‘I 8 on the cam slide, while coarser‘ adjust
ments to effect larger changes in pitch may be se
above described, the mechanism including the
rack IOI, sector I00, piston H12, and cylinder I03
cured by altering the ratio of the gear train in
acts merely to take up lost motion or back-lash
terconnecting the headstock spindle and cam
by insuring that the cam_ 85-86 and the re—
slide. The same set of cam segments 85 and 86
mainder of the cutter-feeding mechanism. will,
can be used alternatively to out either left-hand
during the cutting, operation, never be subjected
or right-hand cams by interposing the idler 61
to a load less than a predetermined minimum. 55 in, or removing it from, such gear train.
In this connection, it is to be noted that the head-l
stock spindle 25 forms an element of the power
transmitting train‘ interconnecting the motor 53
and the drum I8 and that, in conseque??, all
lost motion between the spindle 25 and the drum
is taken up, and maintained taken up throughout
' While I have described my machine above as
adapted to cut a cam-groove in a blank, it will
be obvious that it is equally adapted to grinding
a cam previously out. 'To convert the machine to
a grinder it is necessary only to substitute a prop
erly shaped. abrasive wheel for the cutter 20 and
the cutting operation, by ?uid pressure-in the
to employ a spindle-driving means which will
cylinder
provide an adequate wheel-speed.
I03.
‘
.
'
It has been noted above that the mechanism
I claim as‘ my invention:
'
I00-I03 can be used alternatively in two ways, 65 ‘1,. In a machine for forming generally helical
either to take up lost motion while cutterlfeed
cams, means including a headstock spindle for
ing effort is applied to the drum I8 through the.
rack 9I and. cam 85-86 orto exert the cutter
feeding effort itself and to rotate the drum !8
at a rate controlled by the cam.
The arrange
inent employed to provide operation inthe ?rst
manner has already been described. To provide
for operation in the second manner it is neces
supporting and rotating a cam blank, a rotatable
tool spindle, a tool-spindle support rotatable
about an axis parallel but eccentric to the tool
70 spindle axis, means for driving said tool spindle,
means for moving said tool-spindle support ax
ially of itself to advance a tool in the tool spindle
into and retract it from operative association‘
sary only to reverse the connections between the
with a blank in said blank-supporting means,
cylinder I03 and the conduits I18 and I19‘ and“ 75 mechanism for rotating said tool-spindle sup
auaess ,
16 ~
l5 "
port and headstock spindle in timed relation, and
nism for rotating said tool-spindle support and
control means responsive to advance of said tool
headstock spindle in timed relation, and control
means comprising devices responsive to rotation
and axial movement of said tool-spindle support
spindle support for automatically initiating op
eration of said spindle-rotating mechanism.
2. In a machine for forming generally helical
for causing the machine to proceed automatically
cams, means including a headstock spindle for
supporting and rotating a cam blank, a rotatable
through a cycle including the steps of advancing ,
tool spindle, a tool-spindle support rotatable
means, rotating said support from a predeter
the tool-spindle support, actuating said locking
mined initial position, retracting the support,
spindle axis, means for driving said tool spindle, 10 rotating it reversely to its initial position, and
releasing said locking means.
means for moving said tool-spindle support ax
about an axis parallel but eccentric to the tool
ially of itself to advance a tool in the tool spin
dle into and retract it from operative associa
6. A machine as set forth in claim 3 with the
addition that the means for rotating the head
tion with a blank in said blank-supporting means,
stock spindle and tool-spindle support comprises
mechanism for rotating said tool-spindle support
and headstock spindle in timed relation, and con
trol means controlled by rotation of said tool
a reversible motor, said control means operating
to reverse said motor following the completion
of rotation of the tool-spindle support from its
spindle support for automatically causing said
initial position.
7. In a machine for forming cams and the like,
support-moving means to retract the tool from
20 headstock and tailstock spindles, said tailstock
association with the blank.
spindle being advanceable into and retractable
3. In a machine for forming generally helical
from an operative position in which it cooperates
cams, means including a headstock spindle for
with the headstock spindle to support a blank,
supporting and rotating a cam blank, a rotatable
means operable to bias said tailstock spindle for
tool spindle, a tool-spindle support rotatable
about an axis parallel but eccentric to the tool 25 retraction, locking means for holding said tail
spindle axis, means for driving said tool spindle,
stock spindle advanced, a tool spindle, a movable
means for moving said tool-spindle support ax
support therefor, means for moving said support
from an initial position to cause a tool in the tool
ially of itself to advance a tool in the tool spin
spindle to act on the blank and for subsequently
dle into and retract it from operative associa
tion with a blank in said blank-supporting means, 30 restoring the support to its initial position, a de
mechanism for rotating said tool-spindle support
vice responsive to movement of said support for
releasing said locking means as said support ap
and headstock spindle in timed relation, and con
trol means comprising devices responsive to ro
proaches its initial position, and means also re
tation and axial movement of said tool-spindle
sponsive to movement of said support and oper
support for causing the machine to proceed auto 35 able prior to operation of said last-named de
matically through a cycle including the steps of
vice for actuating said biasing means.
advancing the tool-spindle support, rotating such
8. In a machine for forming generally helical
support from a predetermined initial position, re
cams, means including a headstock spindle for
tracting the support, and rotating it reversely to
supporting and rotating a cam blank, a rotatable
its initial position.
40 tool spindle, a tool-spindle support rotatable
4. In a machine for forming generally helical
about an axis parallel but eccentric to the tool
cams, means including a headstock spindle and
spindle axis, means for driving said tool spindle,
a tailstock spindle for supporting and rotating a
means for moving said tool-spindle support
cam blank, said tailstock spindle being axially
axially of itself to advance a tool in the tool spin
movable into and from an advanced, blank-sup 45 dle into and retract it from operative associa
porting position, means for locking said tailstock
tion with a blank in said blank-supporting
spindle in said advanced position, a rotatable
means, adjustable means for varying the ad-:
tool-spindle, a tool-spindle support rotatable
vanced position of said support, and mechanism
about an axis parallel but eccentric to the tool
for rotating said support and headstock spindle
spindle axis, means for driving said tool spindle, 50 in timed relation.
means for moving said tool-spindle support ax
9. In a machine for forming generally helical
ially of itself to advance a tool in the tool spindle
cams, means including a headstock spindle for
into and retract it from operative association with
supporting and rotating a cam blank, a rotatable‘
a blank in said blank-supporting means, mecha
tool spindle, a tool-spindle support rotatable
nism for rotating said tool-spindle support and 55
about an axis parallel but eccentric to the tool
headstock spindle in timed relation, and control
spindle axis, means ‘for driving said tool spindle,
power-operated means for moving said tool-'
spindle support axially of itself to advance a tool
ing said locking means and maintaining it ac
in the tool spindle into and retract it from Opera-5
60
tuated throughout cam-forming rotation of said
tive association with a blank in said blank-sup
tool-spindle support.
porting means, adjustable means for varying the
5. In a machine for forming generally helical
advanced position of said support, and mecha
cams, means including a headstock spindle and
nism for rotating said support and headstock
a tailstock spindle for supporting and rotating a
cam blank, said tailstock spindle being axially 65 spindle in timed relation.
10. In a machine for forming generally helical
movable into and from an advanced, blank-sup
cams, means including a headstock spindle for
porting position, means for locking said tailstock
supporting and rotating a cam blank, a rotatable
spindle in said advanced position, a rotatable tool
tool spindle, a tool-spindle support rotatable
spindle, a tool-spindle support rotatable about
an axis parallel but eccentric to the tool-spindle 70 about an axis parallel but eccentric to the tool-7
spindle axis, means for driving said tool spindle,
axis, means for driving said tool spindle, means
hydraulic means for moving said tool-spindle
for moving said tool-spindle support axially of
support axially of itself to advance a tool in the
itself to advance a tool in the tool spindle into
tool spindle into and retract it from operative
and retract it from operative association with a
blank in vsaid blank-supporting means, mecha 75 association with a blank in said blankr-support
means automatically controlled in response to
movement of saidtool-spindle support for actuat
2,547,882
17
18
in: means, adjustable means for limiting ad
vance of said support by said hydraulic means,
and, mechanism for rotating said support and
headstock spindle in timed ‘relation.
operative association with a blank in said blank
supporting means, and. reversible hydraulic
means for rotating said headstock spindle and
tool-spindle support in timed relation.
11. A machine as set forth in claim 8 with the
addition that said adjustable means comprises a
PERCY A. NEWMAN.
cam rigid with said support, a cam-engaging
roller, a roller-support, and means for adjusting
‘
said roller-support axially of said tool-spindle
support.
10
REFERENCES CITED
The following references are of record in the
?le of this patent:
UNITED STATES PATENTS
12. In a machine for forming generally heli
ical cams, means including a headstock spindle
Number
Name
Date
for rotatably supporting a cam blank, a rotatable
1,275,985
Bock __________ __ Aug. 13, 1918
and axially movable spindle-support, a tool spin
1,687,260
Ross ______________ __ Oct. 9, 1928
dle eccentrically mounted in said spindle 16 1,871,174
Gruenewald ______ __ Aug. 9, 1932
support, reversible hydraulic means for moving
1,960,460‘
Schurr __________ __ May 29, 1934
said spindle-support axially of itself to advance
2,448,426
Galloway ________ __ Aug. 31, 1948
a tool in said tool spindle into and retract it from
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