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Патент USA US2410026

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- Oct. “29, 1946.
w. F. GROENE ETAL
2,410,026
AUTOMATIC LATHE
Filed Feb. 10, 1943
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06L 29, 1946- -
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AUTOMATIC ‘LATHE
Filed Feb‘. 10,‘ 1943 '
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INVENTORS.
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BY
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ATTORNEY.
Qct- 29, 1946-
_w. F. GROENE v|-:'r AL
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2,410,026
AUTOMATIC LATHE
Filed Feb. 10, 1943
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ll Sheets-Sheet 3
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‘WILLIAM F. GROENE
BY
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‘HARRY C.KEMPER
Oct 29,1946.
w. F. GROENE ET AL
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2,410,026
AUTOMATIC LATHE
Filed Feb. 10, 1945
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11 Sheets-Sheet 4
INVENTORS.
.
BY
‘
WlLLlAMEGROENE
HARRY C..KEMPER
NT'YORHEY.
06L 29, 1946-
w. F. GROENE ET AL
2,410,026
AUTOMATI C LATHE
Filed Feb. 10, 1945
ll Sheets-Sheet 5
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INVENTORS.
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OCt- 29, 1946-
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w. F. GROENE ETAL
2,410,026
AUTOMATIC LATHE
Filed Feb. 10, 1943
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11 Sheets-Sheet e
WILL-MM F. GROENE
Oct 29, 1946-
w. F. GROENE ET AL
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2,410,025
AUTOMATIC LATHE
Filed Feb. 10, 1943
ll Sheets-Sheet 7
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Get 29, 1946.
w. F. GROENE ET AL
2,410,026
AUTOMATIC LATHE
Filed Feb. 10, 1943
11 Sheets-Sheet 8
INVENTORS.
WILLIAM F. GROIENE
umzrq c. KEMPER
AT T ORNEY..
Oct 29, 1945_
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w. F. GROENE ET AL ~
2,410,025
AUTOMATIC LATHE
Filed Feb. 10, 1943
11 Sheets-Sheet r9
INVENTORS.
MHLLIAM F. GROENE
~' HARRY C.KEMPER'
ATTORNEY.
Oct. 29, 1946°
'
W.‘F_'GROENE ETAL
AUTOMATIC
LATHE
Filed Feb. 10, i943
2,410,026
‘
‘
11 Sheets-Sheet 10
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BY
ARRY c. KEMPER
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' ATTORNEY.’ ‘
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Oct- 29, 1946.
W..F. GROENE ET AL
2,410,026
AUTOMATIC LATHE
Filed Feb. 10, 1945
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INVENTORS.
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ATTORNEMY.
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Patented Oct. 29, '1 946
2,410,026
~ UNITED STATES PATENT OFFICE‘
AUTOMATIC LATHE
William F. Groene, Cincinnati, and Harry G.
Kemper, Goshen ,Township, Clermont County,
Ohio, assignors to The R. K. Le Blond Machine
Tool Company, Cincinnati, Ohio, a corporation
of Delaware
Application February 10, 1943, Serial No. 475,342
2 Claims.
(Cl. 82_—-21)
1
This invention pertains to automatic lathes and
is particularly related to the transmission and
control mechanism for such type of lathes. Pri
marily the purpose of this invention is to provide
2
Further features and advantages of this inven
tion will appear from the detailed description ,of
the drawings in which:
‘
Figure I is a front elevation of the automatic
an automatic lathe of completely universal char- ;
acter ‘capable of doing any type or class of work
possible to be machined onsuch a lathe. It is
lathe of this invention showing the general ar
rangement of the base, headstock, tailstock, and
overhead too1 slide.
also the intent to provide in an automatic lathe a
‘
,
Figure II is a rear elevation of the automatic
complete range of speeds and feeds for any type
lathe shown in Figure I.
of material it is desired to machine.
"10 Figure III is a left hand end elevation of the
Another object of this invention is to provide a
lathe shown in Figures I and II.
i
simpli?ed, compact and e?icient feed and rapid
Figure IV is an enlarged fragmentary view
traverse drive transmission for actuating the cut
partly in section of the headstock, control mech
ting tools to and from the work piece mounted
anism, and feed cams for the tool slides shown
in the lathe.
on the line IV—~IV of Figures V and VI.
It is also a further object to provide, in con
Figure V is an enlarged fragmentary transverse
junction with this feed and rapid traverse mech
section through the lathe headstock and bed on
anism, a load-and-?re trip mechanism for al
the line V—-V of Figures 1, IV, and VII, particu
ternately engaging the feed and rapid traverse
larly showing the‘ belt drive transmission to the
work spindle and the spindle stop trip mechanism.
motion at the appropriate time in the cutting
cycle of the machine;
1
Figure VI is an enlarged fragmentary trans
verse section through the lathe headstock on the
Another important featureof this invention is
to provide aseries of tool carrying bars upon
line VI-VI of Figures IV and VII, particularly
showing the feed and rapid traverse drive and
which are mounted the tool holders or slides car
rying the cutting tools so that onelbar extending
longitudinally of the lathe spindle axis is located
directly below said spindle axis for carrying the
turning tools. The second bar is also provided
immediately under and directly below the work
spindle ,and- ?rst mentioned bar for carrying the
control mechanism.
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‘I
i
_
Figure VII is a diagrammatic section through
the transmission mechanism of the lathe head
stock, particularly showing the headstock jdriving
transmission comprising the gear drive and belt
facing tools. The result of this unique arrange 30 drive mechanism for rotating the work spindle
together with the power takeoff mechanism for
ment is to provide much greater clearance room
the feed and rapid traverse movement to the tool
for the chips cut from the work piece in the lathe
slide, shown on the line VII—-VII ‘of Figures V
and at the same time provide much greater ac
and VI.
, ‘
cessibility to both the work and tools of the ma 35 Figure VIII is an enlarged transverse sectional
chine”
.
,
view through the lathe, on the line VIII-VIII of
A further object is to provide in this arrange
Figures I and II, particularly showing the facing
ment of .tool bars extending longitudinal of the
tool on the lower tool bar and the turning tools
.axis of the lathe, one above the other with the
on the upper tool bar of the lathe, together with
1 upper bar mounting the turning tool and the lower 40 the cam actuating mechanism for feeding said
‘,b'ar directly beneath it mounting the facing too1
tools relative to the work spindle, the tailstock for
;feeding devices, means whereby either the front
the
lathe being shown in the background.
,or rear tools may be alternately or simultane
Figure IX is a fragmentary enlarged rear ele
iously utilized for either turning or facing opera
:tions.
45 vation of the universal tool slide'mounted on the
overhead tool barishown by the line IX——IX in
In conjunction Withsuch tool feeding mecha
Figures III, XI, and XII, particularly illustrating
;nism mounted on the bars, one above the other,
the cam actuating mechanism having the con
applicants propose to utilize a_ unique cam actuat
stant feed to depth and dwell position for any
ingmechanism whereby the tools may be brought
,
automatically to a de?nite predetermined depth 50 position of adjustment of» rate of feed.
of cutand dwell while at the same time cam feed
Figure X is an enlarged fragmentary front ele
ingmechanism is fully adjustable to effect any
vation of the universal tool'slide on the overhead
desired‘ rate of feed while at all times retaining
too1 carrier shown by the line X--X in Figures
‘the accurate depth of cut and dwell above men
tioned.‘
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III, XI, and XII.
55
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.
.
Figure X1 is a left hand end elevation partly
2,410,026
3
in section on the line XI—XI of Figures I, II,
IX, and X.
Figure XII is a plan view of the universal tool
4
and 31 are in engagement the gear 31 also en
Figure XIII is a vertical section on the line
gages the gear 40 ?xed on the work spindle 6.
When the gear 37—38 is shifted to the right on
the shaft 39 the gear 38 engages the large face
gear 4| ?xed on the work spindle 6. In this way
two changes of gear drivespeeds may be effected
XIII-XIII of Figures II and IV, particularly‘
showing the feed and rapid traverse clutch shaft.
in the work spindle 6. Thus by this arrangement
the work spindle may be driven directly by belts
slide shown on the line XII—X[I of Figures III,
IX, and X.
vfor the higher smoother speeds required or a gear
Figure XIV is an enlarged detail view of the
cam controlling the rate of feed and dwell for 10 drive having two selections of speed‘ may also be’ ‘
obtained when the gear 3'f—38 is shifted to'the
the various cutting tool slides.
position where gear 31 engages gear 35 of shaft
Figure XV is a view‘ of the pinion shaft for
124 and gear 40 of the work spindle, or when its
setting the cam slides.
gear 31 engages the gear 36 of the shaft 24 and
The lathe comprises a ‘base "I upon which .is
its gear .38, engages the face gear 4| on the work‘
rigidly [mounted a headstock 2 and the tailstock
spindle.
3. The work is held in the lathe 0n the centers
‘In this transmission arrangement it Will be
4 and 5 carried respectively in the headstock work
noted that there are two compartments in the
spindle 3 and the tailstock barrel 1.
lathe headstock, namely the lubricant ?lled com
Referring particularly to Figures III and VII
the work spindle 6 which carries a suitable chuck 20 partment 42 which provides lubricant for the
ing device or work arbor vfor driving the work in
gear transmission mechanism and the dryicom
addition to the center is driven from the main
partment 43 which contains no ‘lubricant and
contains the belt drive transmission as shown
best in Figures V and VII. A suitable lubricant
drive motor 8v which is connected through suitable
belts 9 to the clutch and brake pulley 10 which
incorporates a driving clutch l l and brake device 25 tight ba?ie 44, Figure V, is provided in the bottom
l2 which may be actuatedv by reciprocating the
actuating rod I3 by moving the spool M which
engages the actuating ?ngers I5 in a conven
tional manner, for example, as shown in Patent
of the dry compartment 43 so ‘as vto prevent any
lubricant getting into the belt drive‘ transmission
and impairing its efficiency. Another unique fea
ture of this design lies in the fact that the work
#1,474,-112,~dated November 13, 11923’. Thus main 30 spindle 6 need not be removed from its journal
drive power from ‘the motor =8 and the pulley It)
may be connected to the input drive shaft l6
through the friction ‘clutch H or may be discon
bearings 45 and 49 when it becomes necessary
to replace the belts '26. This is accomplished by
providing the rear mounting bearing 4'! of the
work spindle in a cartridge case 48 which may be
nected from the shaft Is \by this clutch and the
shaft I6 and associated headstock transmission 35 entered into a bore 49 in the headstock housing
2 and held in place by suitable screws 59. When
it is desired to change the belts z?the‘screws 50
On :the shaft 16 is ?xed the gear I‘! which is
arranged in driving relationship with the gear
are removed ‘and the cartridge case 48 and the
lock nut 5| removed from the work spindle. The
48 ?xed on the shaft l9 appropriately jo-urnaled
in the headstock housing '2. The outer right hand 40 clearance thus provided between the bore 49 and
the work spindle is just sufficient to ‘permit easy
‘end-of the shaft [9 extends into a change gear
‘compartment 29 and 'has mounted on it a gear
removal or ‘insertion of the ‘belts through this
opening and around vthe ‘work spindle 6 so that
v2| ‘which ‘may drive the pulley shaft 22 when a
they may then be easily slipped over the ‘pulley
changegear 23 is inserted on the outer end of
25 and the idler pulley 28. The cartridge case
this shaft 22 which meshes with the gear 2-! on
the shaft 49. Or the‘gear 23 may beremoved
48 is then reinserted in the bore 49 ‘and fastened
in placeby the screws 50 to thus provide a totally
and placed on the‘shaft .24 .so that driving power
enclosed integral headstock containing a ‘lubri
'from'th'eshaft .l 9 .may then ‘be transmitted from
cant ?lled gear drive transmission compartment
the gear :21 to the gear 23 on shaft 24 to effect
and a dry belt drive compartment in the same
the'geardrive to the work spindle.
head housing. This arrangement, of course, pro
When belt driving of the lathe spindle .6 is to
vides the utmost simplicity and efficiency inlman
be ,done, :the gear :23 is placed on the shaft 22
ufacturing of a lathe headstock incorporating
whereby driving power from the main drive motor
such features.
'
8 is transmitted to this shaft and to its pulley 25
Power for actuating the cutting tools at feed
which is connected through the belts '26 to a
gearingstop-ped rapidly by means of the brake l2.
pulley 21 fixed to the work spindlev 6 and which
belts may be vkept in proper tension, Figure V,
by vmeans of the eccentric idler adjusting means
comprising a pulley 28 mounted on suitable bear
ings 29 and carried on an eccentric bushing 30
fixedtoan actuating stud ‘3i which'has a squared
end portion 3.2 for application of ‘a wrench for
rotating the stud ,3I to effect adjustment and
tension in the belts '26. A‘ suitable lock nut 33 is
and rapid traverse motion is derived from the
headstock transmission. Referring particularly
to Figure VII, on the shaft i9 is ?xed a gear 52
which drives the gear 53 rotatably journaled on
the shaft I ,6 and which has formed on a sleeve
projecting portion thereof a spiral gear ‘54 and a
second spiral gear 55 ?xed to the other end of
the sleeve of the gear 53. The spiral gear 55
drives a mating spiral gear 59 carried on a shaft
provided for locking the stud :3! in the desired 65 51 appropriately journaled in the headstock
housing ,2. "This shaft '51 proceeds backwardly .to
POSi’QiQIA.
the rear of the headstockinto a change gear com
When gear driving’ of the work spindle 9 is to
partment 58, Figures II and
where it has
be undertaken, gear 23 is placed on the end of
mounted on it a change gear 59 which meshes
the shaft 24 in the compartment 29 whereby the
shaft 24 is. rotated and the double gear 34?xed 70 with another change gear ‘6.9 in this same com
partment '58 mounted on the shaft .61 appropri
thereon and having the gear portions 35 and 3.9
ately journaled in the lower rearward portion of
will thus bedriven. The gear 35 may be engaged
by'the gear 31 when the shiftable gear comprising
the headstock housing 2, Also on this shaft jour
naled against axial movement is the spiral gear
the gears 31 and 38 is moved to the left on the
62 which meshes with the spiral gear 54‘of the
shaft 39 while at'the same time when gears 35
2,410,026
5
‘gear 53 above mentioned. Thus by this arrange
automatically tripped to stop the spindle at a
ment the shaft 6| may be driven at a plurality of
predetermined point in the work cycle from the
diiferent relatively slow speeds or‘ feeding speeds
rotation of the cam drum shaft 'I'I as‘follows:
by changing the change gears 59 and 69 in the
Noting Figure V, on the pin 9| and in the cut
compartment 58 for effecting different rates of 5 away portion 95 formed in the lever 99 is mounted
the lever 96 which has an upward projecting lug
relativevfeed for the tools of the machine. The
91 having a surface 98 engaging the surface 99
spiral gear 62 rotatably mounted on the shaft 6I
is driven at a relatively rapid rate by its mating
of the lever piece 99 but which is free to rotate,
spiral gear 64 so as to e?ect rapid traverse mo
as seen in Figure IV, in a counterclockwise direc
tion. In order to selectively take off either the
feed drive power from the shaft 6| or rapid trav
erse driving power from the spiral gear 62 the ar_
rangement shown in Figures VI and-XIII is pro
vided which comprises a clutch member163 ?xed
tion without effecting rotation of‘ the lever 99.
Rocking the lever 96 clockwise actuates the lever
99 and therefore the control lever 86 to the stop
and brake position‘of the clutch I I—I2. A suit
able compression spring I99 carried on an eye
by suitable pins '64 to the shaft M and having 15 ' bolt I9I and abutting against the nut I92‘ en
gaging the surface I93 of the headstock housing
clutch teeth 65 which are arranged to engage
2 and is connected by means of the pin I94 to the
mating clutch teeth 66 of the output gear 61.
lower end of the lever 96 so as to normally urge
This output gear 6'! is journaled on the shaft BI
this lever 96 in the clockwise or stop and clutch
and has clutch teeth 68 which are arranged'to
engage clutch teeth 69 formed on the gear 62. 20 disengaging position. Also on the lower end of
this lever 96 is a latch piece I95 which is adapted .
Thus by shifting the gear 61 so as to engage the
to be engaged by a mating latch piece I96 ?xed
clutch teeth v66 with the teeth 66 of the clutch
on a lever I9‘! ?xed on the rock shaft I98 jour
member 63 this gear 6‘! will be rotated at feeding
naled in the headstock housing 2. Also ?xed on
speed. Shifting this gear 61 to the left, Figure
the left hand end of this rock shaft I98, Figure
VI, will engage the clutch teeth 69 with the clutch
IV, is the roller arm I99 carrying a roller III]
teeth 69 of the. gear 62 so as to connect rapid
which may be engaged by a dog I I I appropriately
traverse power for rapidly rotating the gear 61.
clamped by a suitable screw II2 on the shaft ‘I1.
This gear 61 is in constant mesh for any shifted
Normally this arm I99 and lever I91 are moved
position with the idler gear 19 appropriately jour
naled on a suitable stud 19a in the headstock 30 so as to constantly be urged toward the‘ latch
piece I95 of lever 96 so that when the lever 86 is
housing, 2. This gear ‘I9 may be connected to or
moved to the position 8619 compressing the spring
disconnected from driving relationship With the
I99 it will automatically be latched by the piece
worm shaft ‘II by means of a pinion ‘I2 slidably
I95 engaging about the piece I96 so as to hold
but drivably mounted on the shaft ‘II by any
this lever in the run position for the work spin
suitable splined connection and may be slid on
dle. As the cam drum thus rotates through the
this splined arrangement by means of the control
transmission gearing to the worm ‘I6 on the shaft
rod ‘I3 having an operating knob ‘I4 projecting
‘H as already described the dog III will rotate
through the front of the base I of the lathe as
around and ultimately strike the roller II9 on
best seen in Figure VI. This worm shaft .‘II has
?xed on it a worm ‘I6 which in turn drives a 40 the lever I99 at the appropriate time in the cut
ting cycle as determined by the setting of the
worm wheel ‘I6 ?xed on the cam drum shaft 11
appropriately journaled in suitable bearings ‘I8
and ‘I9 in the base I‘of the machine, A suitable
crank handle not shown may be placed on the
clutch portion 89 of the worm shaft when the
knob ‘I9 is pushed in against the base I of the
machine as shown in Figure VI so as to rotate
the shaft ‘II manually for effecting manual posi
tioning of the tools for setting the work and tools
prior to the automatic machining cycle. On the
cam drum shaft ‘II are appropriately mounted
the cam drums SI and 82 having appropriate cam
slots 84 and 85 for actuating the various tool
slides in their desired movement.
Referring particularly to Figures IV, VI, and
VII, the control of the clutch II on the input
drive‘ shaft “I6 is accomplished by means of the
main spindle stop and start lever 66 which is
?xed to an appropriate sleeve 91 journaled in the
headstock housing 2 and having ?xed on its inner
end a depending lever 88 which is connected‘ by
means of a link 89 with another lever 99, Figure
V, pivotally mounted on a pin 9I ?xed in the
headstock housing 2 and having a yoked portion
93 carrying a shoe 94 which might be ?tted in
the annular groove 95 of the operating spool I4,
Figure VII, of the clutch II. Thus by moving
the lever from its position 86a, Figure IV, to the
position 861) the clutch spool I4 will be moved to
the left in Figure VII to engage the clutch II;
likewise moving the lever in the opposite direction
will disengage the clutch I I and engage the brake
dog III by means of its adjusting screw II2 on
the shaft TI. Thus when the dog I I I does hit the
roller III! the spindle stop lever will be tripped
to the stop position since the member I96 will
be pulled away from the member I95 by this ac
tuation of the lever I99 allowing the spring I99
to turn the lever 86 to the stop position 9611. It
will be also noted that since the surface 98 en
gages the surface 99 of the lever 99 only from the
clockwise direction of movement that even
though the lever 96 is latched behind the latch
piece I96 of lever I9‘I during the automatic cycle
the stop lever 86 could at any time be moved back
from position 8% to 86a manually to immediate
ly arrest the work spindle rotation in the event
of an accident or any other incorrect operation
of the machine.
The gears 3"I—38 on the shaft 39 may be shifted
axially on this shaft for effecting the two» ranges
of gear driving of the work spindle 6v by means
of-the control lever II3 located on the front of
the headstock as shown in Figure IV. This lever
H3 is ?xed on the rock shaft II4 which passes
co-axially through the sleeve 8'! of the lever 86
and has on its inner end a shifter lever I I5 car
rying a shifter shoe I I6 which engages in the an
nular groove II1 formed in this gear 3'I-—38, so
that rocking of the lever from the position “341
to the position II 3b effects shifting of the gear
to its true driving position as described above.
Feed and rapid traverse power may be alter
nately applied to the cutting tool of the lathe
I21 for rapidly bringing the work spindle 6 to a
automatically at a predetermined position of the
This operating handle and clutch' II may be 75 cutting cycle of ‘the machine.‘ Thisautomaticl
stop.
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2,410,026
7
8
control of the feed and rapid traverse movement
marily for the purpose of accurately positioning
the various levers I28 and I29 with respect to the
is effected from the rotation of the cam drum
shaft 'I'I. Referring particularly to Figures vIV,
V, and _VI it will be noted that the clutch gear
61, Figure VI, has an annular groove I I8 in which
clutch gear 61 so as to provide the proper degree
of accuracy of movement of all of these members
5 during the automatic operating cycle of the ma
is mounted avshoe I I9 which is carried by a yoke
chine.
Referring particularly to Figures I and VIII it
will benoted that extending longitudinally of the
I20 ?xed to the rock shaft IZI journaled in the
headstock 2 of the lathe. On this rock shaft I2I
is mounted a downwardly depending link I22
which has a projecting pin I 23 which may be en
gaged by the screws I24 and I25 of the fork
.shaped lever I26 ?xed on the rock shaft I2‘I
journaled in the headstock housing 2. This rock
base of the lathe is the upper tool supporting bar
10 I44 and the lower tool supporting bar I45 both
located with their axes substantially in a vertical
plane passing through the work spindle axis I46
of the lathe. In this particular exemplary dis
closure the'bar I44 is journaled for sliding and
’ shaft I2‘! proceeds to the left, Figure IV, and has
?xed on its outer end a pair of levers I28 and I29 15 rocking motion in appropriate bearings I47 and
each with rollers I33 and I 3I respectively. The
arm I28 having the roller I39 is engaged and rop
erated so as to rotate the rock shaft I21 in a
clockwise direction by the trip dog I32 while the
lever I29 has its roller I3I engaged by trip dog
_ I 33 which rotates the rock shaft I2‘! in a counter
clockwise direction, as seen in Figure V.
Both of
these dogs I 32 and I33 are respectively clamped
at their desired circumferentially oriented posi
I48 in the base I of the lathe as best shown in
Figure VII and is similarly supported in appro
priate bearings I49 in the tailstock 3. The lower
tool bar I45 is supported in bearings I50 and I5I
in the base I of the lathe and is permitted to
rotate in, said bearings but is restricted from,
axial sliding motion in this particular instance v
by appropriate collars I52 and I53 clamped to the
bar I45. It will be noted that this arrangement
tion on the cam drum shaft ‘IT by suitable clamp 25 of the bars I44 and I45 one above the other and
ing screws I34 and I35 respectively. It will thus
lying substantially in a vertical plane passing
be seen that as the cam. drum shaft 'I'I rotates the
through the axis of rotation of the work spindle
dog I32 will strike the roller I30 so as to cause
that there is no obstruction on either side of this
the rapid traverse motion to take place by en
central vertical grouping of the bars I44 and I45
gaging the clutch teeth 58-459 whereas the shift 30 so that chips cut from the work piece mounted
er I33 when it engages the roller I3I and lever
on the work spindle axis have free access to drop
I29 the feed clutch 65—66 will be engaged to
down past these bars into a relatively wide chip
effect the feeding motion in the cam drum shaft
collecting compartment in the base I comprising
and tool slide of the lathe.
the vertical longitudinally extending rear por
In order that the transition from feed to rapid 35 tions Ia and Ib forming the compartment I c
traverse or from rapid traverse to feed may take
place by snap action motion so that at no time
shall the cam drum shaft ‘ll get to a neutral posi
tion and therefore stop the entire operation of
the machine, a special arrangement is provided
for flipping the clutch gear 61 from one position
to the other. This comprises leaving a substan
tial space for lost motion between the shoe III!
and the annular slot H8 in the gear 61 and in
providing a lever arm I36 having a pin I3'I which
is carried ?xedly to the shaft I2I so as to rock
or swing with the motion of the shaft I2I. A
detent lever I38 having a detent point I39 and
pivotally mounted about the shaft I2‘! is normally
urged into yieldable position against the pin I3‘!
through which the chips readily drop into the
pan I54 below the base I of the machine. Also
since there are no obstructions from these bars
far removed from the vertical plane passing
through the axis of the Work spindle, the operator
is not. interfered with in reaching to the tools and
working from either side of the machine to thus
make apractical machine operation in a line-up
where one operator would operate a plurality of.
; machines and be required to operate the machine
from either side. Also adequate chip space is thus
provided which is a very important feature of a
lathe of this automatic type whichproduces chips
at a very rapid rate during its rapid production
of work pieces.
'
by means‘ of the tension spring I44] attached to
The upper bar I44, while free to rotate, is also
given axial sliding motion by means of the actu
the lever I38 and to a pin IIII ?xed in the head
ating block I55, shown best in Figures VI and VII,
stock housing 2. The point I39 of the detent
which has a slotted portion I56 in which nicely
lever I38 is so arranged that as the shaft I2I is
rocked to cause disengagement of the clutch gear 55 ?ts a collar I 51 ?xed on the bar I44 by a suitable
61 with either of its respective clutches, that the
pin I58 so as to permit the bar I 44 to rotate in
lost motion between the shoe I I9 and the slot I I3
the bearings I41 and I48 of the headstock and
permits the pin I731 to ride a little beyond the
also in the tailstock bearings. In this way the
block I55 accurately controls the axial move
point I39 in the direction it is moving so that
just as the shoe II9 begins topengage the other 60 ment of the bar I 44. The actuating block I 55
side of the slot III3 for removing or disengaging
has a bore I59 which nicely ?ts over the lower
the clutch the remainder of the motion will take
bar I45 and slides thereon so as to support the
block I55 against swinging about the bar I44.
place due to the sliding of the pin I31 down the
surfaces I42 or I43 each side of the point I39 in a
On the lower end of this block I55 is a cam roller
snap action fashion so that the clutch will then
I50 carried on a pin IBI ?xed in the block I55
be moved immediately to disengage one clutch or
and which roller I39 may engage in a cam track
immediately engages .the other series of clutches
84 ‘on the cam drum 8I so that rotation of the
so that at no time is there a position where the
clutch gear 61 is in a neutral or no clutch engaged
position. This is essential in order that the cam
drums on the shaft 1-‘! at all times be rotating in
either rapid traverse or feed so that ‘the trip dogs
III, I33, and I32 may at all times be moved to
effect control of the levers I09, I29, and I123, The
said screws I24 and I25 in’ the lever I26 are pri
drum BI on the shaft 11, through the mecha
nism described, will cause axial displacement of
the member I55 along the lower bar I45 and to
thus‘ cause axial motion in the upper bar I44
through the medium of the collar I51.
Extending longitudinally of the base I and par-'
allel with the work spindle axis of the lathe is the
76 actuating cam slide- I62 carried in suitable guide
2,410,026
9
10
way surfaces I64 and I65, and on the anti-friction
supporting rollers I66 in the Web member Ia of
which engages a cam slot 84 of the cam drum 8I
so that rotation of this cam drum 9i causes slid
ing motion in the cam slide I63 which also car
the base I and the cam slide I63 is carried in
guide ways I61, I68, and on the supporting rollers
I69 in the web portion lb of the base I of the ma
chine in this particular arrangement the turn
ing tools or tools which feed substantially parallel
to the axis of rotation I46 of the work spindle are '
5
ries the cam I99 which thereby actuates the stud
I81 to cause vertical sliding movement in the cam
plate I89 and through the medium of the form
bar I19 bearing against the abutment block I11
to swing the tool holder in the arcuate path of
feeding 291, Figure VIII, to present the tools I14
mounted on the upper tool bar I44 and comprise
a tool slide base I 19 which may be clamped to the 10 to or from the work. This motion may be utilized
bar I44 by means of a clamping screw I1! and
either as performing facing operations with the
which has mounted on top of it a tool slide or
tools I14 or the cam drum 8| may be so arranged
holder I12 having an adjustable screw I13 for
as to effect motion sufficient to merely cause the
accurately moving it to set the cutting tools I14
tool relief in the turning tools I14 from the work
in the tool block I 15 to proper depth and accuracy 15 during their longitudinal return movement.
of out. On this tool slide base I19 is pivotally
Turning motion for the tools I14, that is the
mounted on a pin I16 an abutment ?nger I11
longitudinal or parallel feeding of the‘ tools with
which engages the top surface I18 of the form bar
respect to the work spindle axis I46 is accom
I19. The form bar or plate may be clamped to
plished as above described by longitudinally or
the Vertical cam plate I89 carried between guide 20 axially sliding the bar I44 to which the tool slide
rollers I9I in a bracket I82 ?xed to the base I of
base I19 has been rigidly clamped by the screw
the machine by suitable screws I83. By suitable
I1I through the medium of the block I55 also
bolts I84 passing through clearance holes I85 the
operating on the cam drum 8I. Thus in this
form bar I19 is held on the cam plate and may be
particular exemplary arrangement it is possible
set at any desired adjusted position of‘either par 25 to have facing or radial infeeding of the tools
allel or taper turning by means of the adjusting
I14 with respect to the tool spindle axis or to
screws and nuts I86. The cam plate I89 has a
have longitudinal feeding of the tools along‘said
suitable cam engaging roller pin I81 carried on
axis. Also in instances where pure turning is
a suitable anti-friction ball bearing I88 for easy
to be done the tools I14 are moved parallel to
rotation when bearing against the cam surfaces. 30 the work spindle axis by axially sliding the bar
This roller pin I81 engages in a slot I89 formed
I44 and arranging the ‘surface I18 of the form
in an adjustable cam I99 Which is pivotally
bar I19 in parallel relationship to the work
mounted around a T-slot bolt I 9! held in a T-slot
spindle axis and by so arranging the cam I99
I92 formed in the cam slide I63 so that it may
that it will have no motion effecting the verti
be swung around this T-slot bolt I9I to effect dif 35 cal movement of the cam plate I89 during the
ferent angular positions of adjustment such as
normal turning operations. This cam I99 how
shown in Figure XIV indicated at the I892; posi
ever would in this instance have certain relief
tion of adjustment of the cam slot for a minimum
portions out in it where the cam plate I89 would
of angularity to the cam while the position I99
drop down slightly just after the completion of
shows the steepest position. At the other end of 40 the turning operation on the work so as to re
the cam I99 is out a rack I93 whose arcuate shape
lieve the tools therefrom, during the return
is radially positioned from the axis of pivoting of
movement of the bar I44 in bringing the tools
I14 to initial cutting position.
'
the cam around the T-slot bolt I9I. A suitable“
bore I94 is formed in the end of the ‘slide I63 for
It is also to be noted that taper turning can
- insertion of a pinion gear I95 carried on a shaft
‘ be readily done with this construction by merely
I96 (Figure XV) having an operating‘knob I91
setting the form bar I19 in angular relationship
for easy positioning of the cam I 99 to the desired
to the work spindle axis in proportion to the de
angular setting. A clamp I99 operated by a suit
sired taper to be cut on the work piece. Pure
able bolt I 99 and having a lipped portion 299 may
facing operations would be accomplished with
be tightened to lock the cam I99 in any desired 50 the front tools I14 by merely having the cam
angular position of setting, after which the bolt
plate I99 fully operative to effect vertical move
I9I is similarly tightened to rigidly hold the cam
-ment in the cam plate I99 during which time
for operating the machine.
the bar I44 would be locked against axial mo
Referring particularly to Figure XIV, it will be
tion and would have only rocking motion for the
noted that the portion of the cam embraced by 55 tools I14.
‘
the angle 29I is radially positioned with respect
In this disclosure also is shown a similar set
to the point of pivoting around the bolt I9I and
up for actuating the facing tools which are car
this portion of the cam is so arranged as to give
ried on the bar I45 by means of the facing tool
the proper dwell and accurate positioning of the
holder 291 which may be clamped to the lower
tools to the work and by means of this constant 69 tool bar I45 by a suitable clamping screw 298
radial positioning of the angular portion 29I of
and which has mounted on it a tool block 299
the cam slot I89 the cam may be set to any de_
carrying the facing tools 2I9.
sired angular position of feeding while at the
Similarly this
facing tool holder 291 has an abutment block 2| I
same time always maintaining the same dwell or
mounted on a suitable pivot pin 2I2 which en
?nish position of the tools. When readjusting the ‘35 gages the form bar 2I3 which is similarly held
cam to any desired position of setting along the
into place by screws 2I4 on the cam. plate 2I5
T-slot I92 of the cam slide I63 it may be desirable
and which may be adjusted in the desired posi
in some instances to withdraw the engaging roller
tion by the adjusting screws 2I6, in a fashion
stud I81 which may readily be done by removing
similar to that for the arrangement for actuat
the screws 292 and pulling out the carrying car 70 ing the cutting tools I14. In this instance how
tridge on the stud 293 by means of its manipulat
ever the abutment block 2 II is carried on an ad
. ing handled portion 294 as best seen in Figure
justable piece 2I1 which may be locked in vari
VIII.
oust positions in the arcuate guideway 2I8 by
1 This front cam slide I63 has ?xed on it a roller
means of the clamping bolt 2I9. In this way a
295 carried on a stud 296 ?xed in the cam slide ‘75 greater range of relative positioning of the tools
2,410,026
I
ll
2I0 with respect to the work spindle axis may
be effected along its arcuate path of‘feeding 222.
The cam slide I62 similarly carries a cam 22!
like the cam I9!) just described for the front tool
slide turning tool I14 which actuates a roller pin
222 carried in a suitable anti-friction bearing
12
feed for the cutting tool 228. This cam 241 has
a cam slot 25! which actuates a pin 252 ?xed in
a slide plate 253 having a rack 254 formed in
tegral with it which rack in turn is in engage
ment with a pinion 255 carried on the actuating
shaft 234 and which may be connected to‘ it in
driving relationship‘ through the medium of the
223 in the cartridge 224 held in place by screws
hub 255 to which it is integrally connected when
225 on the vertically movable cam plate 2I5.
the setting screws 251 of the orienting coupling
This cam slide I52 similarly has a roller like
that of the cam slide I63 indicated at 225 car 10 258 are properly clamped. The outside portion
259 of the coupling 258 can be positively attached
ried on a'stud 221 (Figure VI) which engages in
to the actuating shaft 234. The purpose of this
a suitable cam track 84 in the cam drum 8!.
coupling 258 is to permit the proper orientation
In this instance of utilizing the rear tool holder
of the pinion and rack with relationship to the
221 on the bar I45 primarily for facing or ra
cam for starting the tool at the right end of the
dial infeeding of the tools 2Iil along the arcuate
desired position for beginning the cutting opera
path of feeding 220, bar I45 is con?ned against
tion.
I
axial movement by the collars I52 and I53 and
On the other end of the actuating shaft 234
that purely vertical motion in the cam plate 2!?!
is ?xed a pinion 25E] Figures X and XI which
effected through the medium of the roller pin
222 and movement of the cam slide I52 by the 20 drives a mating pinion 25! carried on a suitable
stud v2I52 ?xed in the base plate 233 and driving
cam drum 8! is utilized. It is to be further
a rack 253 fixed on the tool slide 23!}. A suitable
noted that in this particular arrangement be
compression spring 234 is used to normally force
cause of utilizing the lower bar M5 for racing
the tool slide away from the work piece to at all
rather than the front bar, that lesser arcuate
times take out any slack between the rack and
path of feed 2253 is provided and a greater range
pinion and cam driving mechanism just described
of facing may thus be undertaken. By main
during the turning operation and to prevent the
taining the bars I44 and I45 substantially in the
tool slide 235 and the tools 228 from dropping
same vertical plane passing through the work
down toward the work piece when cutting action
- spindle axis the chips are easily disposed of as‘~
is relieved therefrom and which would other
they drop‘freely into the pan of the lathe and
wise make it dif?cult to do accurate ?nishing with
also easy accessto the cutting tools is thus pro
vided from either side of the machine.
The cam drum 3! is designed with appropri
ate cam slots (not here shown in detail as this
mechanism is readily understood and well known
in the art) for actuating the block I55 and the
cam slides I53 and I52 in appropriate sequential
this cutting tool. This is accomplished by spring
264, engaging in the upper portion 255 of a suit
able bore 266 formed in the slide 233 and bearing
against a guide block 261 rigidly ?xed to the
base plate 232 by suitable screws 268. It can thus
' be seen that as the cam slide 246 is moved'back
or forth in the guideways 245 its cam actuating
relationship to effect the various operations de:
means and roller pin 252 will rotate the shaft 234,
sired of the lathe of both tool reliefs and feed
motion either radially into the work for fac 40 the rack .2 54 and pinion 255, and the pinions 25!]
and 26! which actuate the rack 263 ?xed on the
ing or longitudinally of the work for turning.
slide 230.
'
In addition‘ to the cutting tools IIII and 2!‘..3
The cam slide 245 is actuated in its guideways
just described there may be provided additional
245 from the cam drum 82 mounted on the cam
tooling comprising the cutting tools 228, Fig
ures I, XI, and XII carried in appropriate tool 4k 31 drum shaft ‘I’! as best seen in Figures II, III, and
IV. The shaft 1'! is supported at its outer end
block 229 mounted on a vertical universally
in, a suitable bearing 259 in a bracket 21!] ap
mounted tool slide 23%}. This tool slide 232 is
propriately ?xed to the left hand end of the
>mounte-d on suitable dovetail guideways 23! and
base I of the machine by suitable screws 21'!
232 on a base 233 which is mounted on a swivel
around the axis of an actuating shaft 232 appro
priately journaled in the supporting housing 235'
to which the base plate 235 is fixed by means of
best seen in Figure III. On the tool supporting
bars I44 and I45 is slidably mounted the actuat
ing block 212 having a downward depending roller
suitable T-slot bolts 231 operating in a concen
223 carried on a suitable pin 214 ?xed inthe ac
tric annular T-slot 233 formed in the base plate
236. This base plate 235 in turn is mounted to
the overhead tool supporting rail 23% by suitable
tuating block 212 and which roller 213 operates
T-slot bolts 246, as best seen in Figure XI. In
this way the tool slide base 233 may be set to
; in an appropriate cam slot 85 formed in the cam
drum 82. By this arrangement the block 212
is slid along on the bars I42 and I45 independent
of any motion these bars may have.
On' one
side of the block 212 is provided a pair of lugs,
any desired angular position so that the cutting
tool 228 may be fed at relatively steep angles 60 Figure II, forming a slot 215, in which operates a
for cutting such work as bevel gear blanks and
the like.
shoe 215 ‘carried in the end of a lever arm 211.
‘and guided in the guideway 245 as best seen in
Figures II and IX is the cam slide'245 which
carriesv an actuating cam 24'! of similar design
to that of the cams I93 and 22!, Figure VIII,
already described. This cam may similarly be
The outer end of the bars I 44 and I45 adjacent
the blocks H2 is supported by a supplemental
bracket 21% carried on the bracket 219 ?xed to
7 the end of the base I of the machine. In this
way support is given to the tool bars I44 and
I45 for holding the actuating block 212 in proper
operative position relative to the cam drum 82.
The lever 211 connected through the sleeve 215
to the actuating block 212 is mounted on a pivot
pin 229 held in a bifurcated downwardly pro
jecting integral support portion 289 of the over
head rail or tool supporting member 239 and has
adjusted by manipulating the clamp bolt 249
and its clamp 25!] for setting the desired rate of
in its upper end a shoe 28! which operates in an
' elongated cross slot 282 formed in the cam slide
This overhead tool supporting rail 239 is mount
ed on the headstock by suitable means such as
the bolts 24! and is carried on a pedestal 242
appropriately mounted on the tailstock by screws
243 and connected to the overhead rail by screws
244. In this overhead tool supporting rail 239
'
2,410,026
13
246 so that as the cam drum 82 rotates it will
slide the actuating block 212 along on the bars
M4 and I45 thus rocking the lever 21‘! and thereby
sliding the cam slide 246 in the member 239 to
effect feeding of the cutting tool 228 to and from
the work piece in the lathe. It is to be further
noted that the cam 82 is mounted on the same
shaft as the cam drum 8| so that all of the
cutting tools including the cutting tool 228 mount
14
said second axis, a form bar adjustably mounted
on ‘said plate means, to contact and pivot said
holder about the axis of said bar, a cam slide
means on said lathe, translatable parallel to said
axes, and a connection between said'slide means
and plate means, said connection including a
cam pivoted on one said means and a pin on the
other of said means adapted to coact withsaid
cam to variably transmit motion from said slide
ed on the tool slide 230 may be operated in a 10 means to said plate means.
predetermined sequential relationship relative to
2. In a lathe having a base, a headstock and
one another. By appropriately setting the swivel
a tailstcck on said base having centers to receive
slide 233 around to any desired position the cut
and rotate a work piece upon a ?rst axis, in
ting of any steep range of tapers desired with
combination, a tool bar mounted for pivotal and
this overhead tool feeding arrangement may be 15 axial translation in said stocks on a second axis
undertaken.
parallel to said ?rst axis, tool holder means ad
Having fully set forth and described our in
justably secured to said bar, a plate guided for
vention what We claim as new and desire to se
translation on said base in a direction spaced
cure by United States Letters Patent 15:
from, and normal to said second axis, a form
1. In a lathe having means for receiving and 20 bar adjustably ?xed to said plate and having a
rotating a work piece about a ?rst axis, a bar
journaled for rotation on a second axis parallel to
said ?rst axis, a tool holder adjustably secured
to said bar and adapted to hold a tool in cutting
cam edge engaging said holder, a cam slide in
said base, adjustable cam connections between
said slide and plate, and a single means having
a cam slot therein connected to said bar to e?ect
engagement with a work piece in said lathe, plate 25 translation of said bar and said slide.
means guided for translation on said lathe in a
WILLIAM F. GROENE.
direction spaced from and angularly related to
HARRY C. KEMPER.
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