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Патент USA US2078696

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April 27, 3937»
E. J. SVENSON
HYDRAULIC MATERIAL WORKING APPARATUS
Original Filed Sépt. 15, 1930-
e Sheets-Sheet 1
April 27, 1937.
‘
E. J. SVENSON
2,078,696
HYDRAULIC MATERIAL WORKING APPARATUS
Original Filed Sept. 15, 1930
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HYDRAULIC MATERIAL WORKING APPARATUS
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E. J. SVENSON
HYDRAULIC MATERIAL WORKING APPARATUS
Original Filed Sept. U13, 1930
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Patented Apr. '27, 1937 -
UNlTED’ST-ATES PATENT OFFICE
2,078,696
HYDRAULIC MATERIAL WORKING
'
APPARATUS '
Ernest J. Svenson, Rockford, Ill.
Application September 13, 1930, Serial No. 481,142
Renewed February, 3, 1937
10:; Claims.‘ _ (c1. n+2)
My invention. relates generally to hydraulic
material working apparatus, and'more particularly to apparatus such as automatic lathes andthe like which are equipped with hydraulic 5315-.
rect ?uid from a'suitable source of supply to
the hydraulic mechanism which controls vthe
actuation of a second hydraulic mechanism, and
in another shifted position serves to direct ?uid
5- tems of control.
for rapid traverse purposes to both of said hy- 5
In using conventional types of material work- draulic mechanisms. In other words, my inven
ing apparatus, such as automaticlathes having. tion contemplates the provision of a system of
a plurality of movable tool carriages, consider- control for a plurality of hydraulic actuators,
able dii?culty has been experienced in controlling in which a valve serves to initially direct ?uid
10 the movements of tOOlS- This fact is particularly to one of the actuators only, and subsequently 10
true in connection With the hydraulic control of . to direct fluid to all of the actuators in order to
a plurality of carriages. In other words, it has
e?ect rapid reverse- traverse of‘ said actuators.
. been found di?icult to control the movements of
Another object of my present invention is to
a plurality of machine carriages so that each
15 carriage is moved to a predetermined position
provide, in combination with the hydraulic sys
tem of control above set forth, a plurality, of lit
with respect to the other carriage or carriages
} during a predetermined interval of time.
It is one of the primary objects of my present
closed hydraulic circuits, whereby feeding move
ment isv imparted to the actuators.
In addition to providing improved hydraulic
, invention to overcome difficulties heretofore ex- ' circuits, my invention contemplates the pro
20 Derienoed by Providing ehydmulie System Of 0011trol which will serve to accurately and positively
vision of improved mechanical control devices, 20
whereby the shifting of carriages, such as the
position one carriage with respect to another
durin‘g each successive cycle of operation of the
front and rear carriages of a lathe, may be et
fectively governed,
'
The foregoing and numerous other objects and
advantages will be more apparent from the fol- 25
machine.
25
-
More specifically, it might be Stated that my
invention contemplates the provision of a new
lowing detailed description when considered in
connection with the accompanying drawings,'
and improved hydraulic system of control which
is so arranged that a plurality of shiftable tools,
as for example, tools on front and rear carriages
"30 of an automatic lathe. may he brought into engag'ement with a rotating Work piece at a Proper
predetermined time during each successive cycle
of operation of the machine.
7 _
wherein_
'
F
-
Figure 1 1s .9, plan‘ View of an automatic by.
draulically controlled lathe which is constructed 30
in accordance with'the teachings of my present
invention;
. ,
Figure 2 is an enlarged plan view 01' the dog
‘ Another object of my present invention is to ' carrying slide and associated valve mechanisms,
35 provide in a hydraulic system of control as - a portmn of said structure being shown in section 35
above Set forth, a singledcontml means Pf ex‘
‘ tremely simple and practical construction, whereby the movements of ‘the hydraulically operated
machine parts may be conveniently controlled.
40 In order to bring about the above mentioned
in order to more clearly set forth the general ar
rangement thereof;
Figure 3 forms a continuation of Figure 2 and
discloses fragmentaruy the portion. of the rear
11d
ewed alon the une
40
accurate control of the movements of a plurality
ggoll?g‘gga?e S
°f machine camages- or the ‘like’ I propose to so
arrange the hydraulic system of control that the
hydraulic mechanism for‘ Shifting one carriage
Figure 4 is a fragmentary vertical sectional
_
view taken longitudinally of .the slide substan
45 is controlled directly ‘by the mechanism which
hydraulically actuates another carriage. ' In
other words-1 propose to operate one of‘ Said
' hydraulic mechanisms directly in ggspcnse‘ to
e as! w
_
g
“any along the line 4-‘ of Flgm'elza
H.
f th 45
Figure 5 is 8' transverse-“M10113 1.3V ° 1 8
rotary control valve for the front ca age 0 r
cult, said view being taken substantially along
the actuation of another carriage operating
50 mechanism,
'
the line 5—50fF1E111‘e 2;.
.
>
Figure 6 is a transverse vertical sectional view 50
‘A still further object or my present invention
is to provide, ‘in combination with the hydraulic
system of control just set forth, an improved
control valvev of extremely simple construction,
'55 said valve in one shifted position serving to di-
of the control valve and the associated Portion!
of the dog carrying slide, said view being taken
substantially along the line 6-8 of Figure 2;
Figure 7 is a transverse-vertical sectional view
taken along the'line 1-4 of Figure 8;‘
‘5.5..
25";
2,078,696
Figure 8 is a horizontal sectional view taken
substantially along the line 8--8 of Figure '7;
Figure 9 is a transverse sectional view of the
control valve taken substantially along the line
tion thereof with my improved hydraulic system
of control so as to clearly set forth at least one
Figure 10 is a similar transverse sectional view
taken along the line Ill-l0 of Figure 8;
Figure 11 is a fragmentary detail sectional view
practical application of my invention. In order
to more readily understand my present invention
I shall ?rst proceed to brie?y designate certain 5
structures of the lathe, and subsequently de
scribe these structures in connection with my im
proved mechanism for‘ controlling the operation
of the unbalancing mechanism, said mechanism
of these lathe elements.
9-9 of Figure 8;
-
'
10 being shown in position to unbalance the fluid
pressure within the chambers of the valve mecha
nism shown in Figure 8;
Figure 12 is a transverse vertical sectional View
of one of the variable displacement, high pressure
plunger pumps which is employed for feeding
purposes, said .view being taken substantially
along the line I 2—|2 of Figure l;
'
Figure 13 is a transverse vertical sectional view
of said pump taken substantially along-the line
I3—l3 of Figure 12;
_
Figure 14 is a fragmentary end elevational view
of the automatic lathe as viewed from the left end
of Figure 1;
Figure 15 is a central transverse sectional view
25 of the check valve which is employed in the low
pressure ?uid circuit;
Figure 16 is a circuit diagram of my improved
,
'
Referring to Figures 1 I. and 14, it will be seen
that I have disclosed an automatic‘ lathe which
includes a suitable base or bed 30, which sup
ports a head stock designated generally by the
numeral 32, and a tail stock which is designated
generally by the numeral 34. Mounted within
this head stock 32 is a suitable work spindle 36,
and this spindle 36 is connected with and driven
from a clutch mechanism 38. This clutch mech
anism 38 serves to connect and disconnect the
spindle 36 with a suitable source of power sup
ply, for example, with an electric motor 40 shown
20
in Figure 14. This electric motor 40 is. con
nected with a rear drive shaft .42 through the
agency of a suitable chain belt 44. Thus, the
motor 40 may be continuously operated so as to > '
rotate the drive shaft 42fI and when it is desirable,
power from the drive shaft 42 is imparted to the
hydraulic system of control, said system includ- ' spindle 36 by manipulating the clutch mechanism
ing the double control valve structure shown in
30 Figures 6 to 10 inclusive, said valve being shown
in neutral position;
Figure 1'7 is a sectional view of the valve
I mechanism similar to the section shown in Fig
ure 16, disclosing the rapid approach position of
said valve mechanism;
I
Mounted upon the front side of the lathe is a 30
tool carriage which I have designated generally
by the numeral 46. This carriage ,46 is clamped
at its lower end upon a cylindrical bar 48 and
is capable of being oscillated with the bar 48
about the axis thereof‘ toward and away from‘ '
Figure 18 is a similar view disclosing the re
a work piece (not shown), which work piece ~is
verse rapid traverse position of said valve mech
adapted to be supported between the tail stock
amsm;
,
34 and a face plate 36a of the spindle 36. This
'
‘Figure 19 is a transverse sectional view similar
to Figure 6, of a modi?ed control valve;
Figure 20 is a horizontal sectional view taken
substantially along the line 20—2ll of Figure 21;
' Figure 21 is a vertical section of the control
45
38.
valve taken substantially along the line 2|—2l
of Figure 20;
Figure 22 is a transverse section of the valve
mechanism taken substantially along the line 22
22 of Figure 21;
'
front carriage 46 includes an upper slide 50
which is adjustable toward and away from the 40
workpiece by__means of a suitable screw 52, and
this slide supports a suitable tool 54.
The oscil- '
lat-ion of the carriage 46 with the support bar
48 is controlled by means of a'hydraulic mecha
nism or actuator which Ihave designated gener
ally by the numeral 56 in Figure 16. This ac
tuator 56 is positioned immediately beneath ‘the
outer end of the carriage 46, and includes a cyl
tional view taken along the line 23-23 of Figure
inder 58 which reciprocably supports'a piston '60.
This piston is vertically reciprocablewithin the
21;
cylinder 58 and is mounted upon a suitable pis- .
Figure 23 is a similar transverse vertical‘ sec-_
Figure 24 is also a transverse sectional view I ton rod 62 which extends von both sides of said
taken along the line 24--24 of Figure 21; and '
Figure 25 discloses a shifted position of the
55 ,unbalancing device of Figure 20.
The upper extremity of the piston rod 62 sup
ports the free extremity of a guide bar 64 which
Referring now to the drawings more in detail,
it will be observed that like numerals have been
is pivotally mounted at 66 on the front side of
the machine in any suitable manner. The upper
employed to designate similar parts throughout
surface of the guide bar 64 serves as a rest for
the outer portion of the oscillatory front car
riage 46, as shown fragmentarily in Figure 16. 60
Obviously, when the piston 62 experiences‘ an
the various ?gures.
60
piston.
'
For the purpose of disclosing one practical ap
plication of my hydraulic system of control, I
have selected an automatic lathe, which is clear
ly shown in plan in Figure 1.
This lathe is structurally similar in many re
65 spects to the lathe which is described and claimed
in my- co-pending applications, Serial No. 391,130,
?led September 9, 1929, and Serial No. 439,306,
?led March 27, 1930, and therefore a detailed de
scription of the various elements which consti
70 tute the lathe'structure proper is not essential
to a complete understanding‘of the present inven
tion.
.
However, enough of the structures of the lathe
elements are disclosed in the present application
75 -to enable a clear understanding of the co'mbina;
upward movement, the carriage 46 will be swung ,
with the support bar 48 so as to carry the tool
54 into operative association with the work piece.
Longitudinal movement of the tool 54 'and' the
carriage 46, upon which it is mounted, is occa
sioned in response to the actuation of a hydraulic ~
mechanism or actuator 66-, Figures 1 and 16.
This actuator 68 includes a cylinder 10 and a
piston 12 which is horizontally reciprocable '
within said cylinder. A piston rod 14 serves to
connect the piston ‘I2 with one extremity of the
cylindrical bar 48. Thus, when movement is‘ ex
perienced by the piston ‘I2, a corresponding lon
gitudinal movement will be imparted thereby to
3
2,078,696
the bar 48, and this bar, as set forth above, car-i drawn during the compression stroke of the pis
ries the carriage 46.
tons through passageways I 32 which register with
'
a peripheral valve port I36. This port commu
nicates with a pipe line I38 through the agency
of a valve passage I40. The tapered valve I22, $1
The automatic lathe also includes a rear tool
carriage which I have designated generally by
the numeral 16. This tool carriage includes a
slide 18 which is recipfocable upon a guide frame
80, Figures 1 and 3, toward and away from the
CI
is secured against longitudinal displacement to
. work-piece. ‘The slide 18 also supports a tool
the right, Figure 12, by means of an antifriction
thrust bearing I42 and an abutment screw I44.
82, and by means of a suitable screw _84, Figure
1, the slide 18 may beadjusted toward and away
This tapered valve I22 positively prevents leakage
of ?uid to the left along the surface thereof, and 10
thus renders the pump particularly adaptable for
use in connection with closed ?uid circuits. In
other words, the pipe lines I24 and I38 form two
sides of a closed circuit, about to be described.
15 anism or, actuator which is designated generally
These pumps 84a, and 94 respectively are adapted
by the‘numeral 86. ,This actuator includes a to supply fluid at high pressure to the actuator
cylinder 88 and a piston 90, which is horizon
68, which longitudinally moves the front tool car
tally reciprocable within said cylinder. A piston riage, and to the actuator 86 which moves the
rod 92 is provided for the purpose of connecting rear tool carriage transversely of the work piece.
20 the piston with the slide 18. Thus, it will be
' A reservoir I46 positioned at the upper portion 20
apparent that the actuator 56 controls the 0s.
of the machine contains a supply of ?uid, and
cillation of the front tool carriage, while the ?uid from this reservoir is directed through a
from'the work piece. This carriage 16 is ar
ranged to move said tool transversely of the work
piece. Movement. is imparted to the slide 18
.through the agency of a suitable hydraulic mech
' actuator 68 controls the longitudinal movement '
of said front carriage, and the actuator 86 con
25 trols the transverse reciprocation of the rear too
carriage 16.
_
,
Pumps
N,
Mounted upon the upper portion of the head
stock 32 is .a pair of ?uid propelling mechanisms
30 or pumps 94 and 9411.
These pumps are identi
cal in structure and the pump mechanisms per
se do not form a part of the present invention,
except as said elements enter into the general
combination of my improved hydraulic system of
35
control.
Referring to Figures 12 to 14 inclusive, it will
be seen that each of these pumps includes a‘ cen
tral casing 96, an end casing member 98 on one
side thereof, and a second casing section I00 se
40 cured to the opposite side of the central casing
96- This casing section I00 provides a support
for a plurality of radial pistons I02, and move
ment is imparted to these pistons through the
the purpose of imparting rapid movement thereto.
.
Control valve
anism I56, and in order that the operation of
this valve mechanism may be more readily under
stood, 1 shall describe the same in connection
with the ?uid circuit which includes the actuators
66, 68, and 86. This valve mechanism I56, as
clearly shown in Figures 1 and 2 and Figures 6
to 11 inclusive, is mounted upon the front side
of the machine and is located in a convenient
This I position for manual manipulation by the machine
driving ring I08 is mounted on anti-friction bear
ings supported by a rotatable driving member
I06, and this driving member is driven by and
laterally adjustable within a sleeve member I08.
Keyed to this sleeve member I08 is an annular
50, sprocket H8, connected ‘by means of a chain
I I2 with a companion sprocket H4, Figure 14,
which is mounted upon the work spindle 36.
v'I'hus it will be apparent that the pumps 84 and
- 84a are driven directly-from the work spindle
of the lathe.
3
The driving ring I04 of each of the high pres
do
I50. Fluid from the discharge side of the gear
pump‘ I50 is directed through a pipe line I52 to 10 GI
the intake port I54 of a valve mechanism which
I have designated generally by the numeral I56.
This gear pump I 50 is constantly driven from the
shaft 42, asclearly shown in Figure 14, and pro
vides the means for supplying low pressure ?uid 30
at increased displacement to the actuators for
~ I shall now proceed to describe the valve mech
.
agency of a driving ‘ring or annulus I04.
-
pipe line I48 to the intake side of a gear pump
operator. Manual manipulation of this valve is
controlled through the agency of a control handle
I58, and this control handle serves to reciprocate
valve members I60 and I62 which are movable
within a casing I64. The valve members I60 and
I62 are also adapted to be automatically shifted 50
within the casing and this automatic control will
be later described. One end of the casing I64 is
closed by a. cover plate I66 and the opposite end
is closed by a cover plate I66. This cover plate
I68 is provided with a boss I10 which serves as
means for supporting a balancing mechanism
sure plunger pumps may be laterally adjusted . I12, which will be described later.
The left extremity of the valve member I60 is
by turning an adjusting nut II6. This nut ‘is
connected with a cylindrical member II8 which pivotally connected to the lower end of a crank
is provided with an angularly disposed projection I14, and the left extremity of the valve I62 is 60
I20 which extends into a companion opening in connected to a similar crank I16. The upper
the driving member I06. Thus, by rotating the portion of these cranks are mounted upon sleeves
H411 and‘ I‘I6a. respectively, Figure 6, and these
nut II6, the eccentricity of the driving ring I04
may be varied. The casing section I 00 also serves
65 to support a tapered rotary valve I22 which is
adapted to control the ?owof ?uid toward and
away from the outer ends of the pistons I02.
Fluid is directed into the pump through a pipe
I24which communicates with a chamber I26,
and from this chamber ?uid passes through a
valve passage I28 to a peripheral valve port I30.
This valve port I30 "successively registers with
radial passageways I32 which communicate at
their outer-extremities with chambers I34 at the
75 outer ends of the pistons I02. Fluid is with
sleeves are, in turn, mounted upon a shaft I18
which extends on opposite sides of the valve
casing I64. The cranks I14 and I16 are secured
to their respective sleeves by means of suitable.
pins I80. The control handle or lever I58 is
secured to the outer end of the sleeve I16a by
means of a pin I82, and the outer extremity of
the sleeve I14a. supports a block I84, which is
formed with a pair of dog engaging ?ngers I86
and I88. These ?ngers cooperate with mecha
nisms later to be described, for automatically
controlling the shifting of the valve members.
2,078,696 1
,
A nut I90 carried at the outer extremityof the single outlet port, namely, the port 2 I 4 and thence
shaft H8 is adapted, when tightened in position, through the pipe line 228.
.
‘ Fluid entering the cylinder 58 causes the pis
to urge the sleeves I'I4a and H642. into ?rm abut
tion 60 to move upwardly, thereby effecting the
ment, and thus bind said sleeves and shaft to
4s ,
5 gether as a unit. When these sleeves and shaft
are thus secured, movement of the single control
handle I58 will cause the simultaneous actuation
of both of the valves I 60 and I62. If it is de-,
sirable to manually operate one of the valves
swinging of the front tool carriage 46 and its sup
ported tool. 54 toward the work piece. Fluid from
the advancing side of the piston \60 passes out of "
10 independently of the other, it is only necessary
to loosen. the nut I90. It will be noted that the
block I84 is provided with a knurled upwardly
one end of a check valve 232 of improved prac
extending handle I84a, which serves as a con-v
venient means for manually manipulating said
15 block.
‘ -
‘
the upper end of the cylinder 58, Figure - 16,
through a pipe 230, and this pipe connects with
tical construction, which will be described later
in detail. It will suffice to say that this valve 232
prevents the reversal of ?uid ?ow into the pipe
230. The other end of the check valve 232 con
nects with a pipe 234, and this pipe is connected
to one extremity of acylinder 236 of a hydraulic
In Figures 6 to 8 inclusive, as well as Figure-16,
I have shown the valves I60 and I62 in their. clutch operating mechanism, which I have desig
neutral position. When these valves occupy this nated generally bythe numeral 238. vFluid enter
neutral position, it 'will be observed, by referring ing the cylinder 236 from the pipe 234 passes out;
20 particularly to Figures 8 and 16, that ?uid from ~ wardly through a pipe 240, which connects with v20
one extremity of the cylinder 88. Thus forward '
the low pressure pipe line I52 will pass through
the intake port I54 of the valve casing, and thence 'movement is imparted to the piston 90 in the
cylinder 88 in response to- the upward movement
into a passageway ' I92, and it will be seen by re
of‘ the piston 60. ‘In this manner I am able to '
ferring‘to Figure 9 that this passageway I92 ex
tends from one side of the valve casing to the
other, or, in other words, encircles both of the
valves I60 and I62. In this neutral position of
the valve members, the passageway I92 com;
municates with radial ports I94 in the valve I60
30 and similar ports I96 in the valve I62. The ports
I94 communicatewith a central longitudinal valve
passage I98 which opens into an end chamber '
200, while the radial ports I96 communicate with
a similar longitudinal passage 202 which opens
' into a chamber 264. These chambers 200 and
' 204 are connected to a pipe line 206, and them)
per end of this pipe line is connected to~a mecha'—
' nism 208 having an adjustable restricted orifice.
Fluid ‘passes through this restricted ori?ce and
Thus, it
40 is thus returned to the reservoir‘ I46.
will be apparent that, when. the valve members
occupy their neutral position, ?uid from (the'low
pressure source of supply will circulate there
through and will not be distributed through any
45 of the ports 2 I0, 2I2, 2“, and 2 I6 provided within
the valve casing I64. It will be noted that the
ports 2") and 2I2 are closed by the valve sections‘
2I8 and 220 respectively, while the ports 2I4 and
2I6 are closed by valve sections 222 and 224 re
50 spectively.
'
'.
Consider now that the valve members are
cause the piston 90to move a-predetermined dis 25
tance during a corresponding movement of the
piston 60. Fluid from the advancing side vof the I
piston 90 passes outwardly through a pipe'242
which connects with the valve port 2I2. At this
time the valve port 2I2 communicates with an 30
annular port or passage 244 of the valve member
I60, Figure 17, and this port 244 communicates
with a passageway 246, Figure 7, provided within
the valve casing I64. This passageway 246 opens
at its opposite extremity into the chambers 200
and 204; and thereby the ?uid is returned through
,the pipe 206 to the reservoir I46.
v‘At this point it should 3be noted in Figure 16
that the left end of the cylinder 236 of the hy
draulic clutch control mechanism 238 is connected
40'
to thepipe 242 by means of a pipe-248. Thus,
when the valve members are initially shifted to
their rapid approach position shown in Figure 17,
a piston 250 within the actuator cylinder 236 will
be urged to the left, and ?uid from the advancing
side of this piston will be returned through the
45
pipe 248. The piston 250 through its piston rod
252is-connected with the clutch mechanism 38
as shown; in Figure 1, 'and the movement of this '
pistonto the left will actuate said clutch mecha 50
nism so as to establish a driving connection be
shifted to the position shown in Figure 1'7‘, which tween the work spindle 36 and the drive shaft 42.
will hereinafter be referred to as the rapid ap _ This causes the pumps 94 and 94a to be actuated.
proach position. In this position low pressure Fluid from the discharge side of the pump 94,
?uid from the pipe line I52‘ passes through the Figure 16, passes through the pipe I38, which
valve port I54 and intothe passageway I92,vas' connects with the outer end of the rear carriage
previously described. However, when the valves ' cylinder 88. The return pipe I24 connects the '
occupy this shifted position, the radial ports >I94’ , intake side of the pump 94 with the opposite
and I96 thereof are closed, thereby preventing the extremity of the cylinder 88; The discharge side
60 circulation of incoming ?uid through the longi— of the pump'94a is connected through a pipe>i258 60
tudinal passageways I98 and 202 back to the with the right end of the cylinder ‘I0 ‘of the actua
reservoir I46. The incoming'?uid, however, is 'tor,68. The opposite end of the cylinder ‘I0 is
directed througha ‘lateral port226 in the valve connected through a pipe 260, a rotary valve 262,
member I62 to the port 2I4, and from this port and a ‘pipe 264 to the intake side of the pump
94a.~ A pipe line 266 serves to connect the pipe 6.5
Fthe'?ui'd is conducted through a, suitable con
55
duit or pipe 228 to the lower extremity of the
cylinder 58 of the actuator 56. It is to be noted
that, when the valve members occupy this rapid
approach position, the section 2| 8 oflthe valve
. member I60 closes the port 2"), thereby prevent- _
line 264' with the upper end of the cylinder 58 of
the actuator 56, while a pipe 268 serves to con
nect the lower end of said cylinder with the
pipe 258.
.
'- From the foregoing it will be understood that
70'
when the valves I60 and I62 are simultaneously '
ing the low pressure ?uid from passing outwardly
through ‘said port. In other‘ words; when the
valve members occupy the positionsho'wn in Fig
shifted from the neutral position shown in Fig
me 16 to the position shown in Figure 17, the
75 ure 17,.fiuid is directed by the valve through a
'cause; the rapid approach of the fronttool. 54
actuators 56 and 86 will be operated so as to
75
5
2,078,696 ~
and the rear tool 82 toward the work piece.
During this operation, ?uid such as oil, passes
outwardly through a single port, namely, the
port 2I4, Figure 1'7, through the pipe 228 and
.01 into the cylinder 58, Figure 16. The ?uid from
their advancing feeding movement, the valve '
members I 68 and I62 are moved to the rapid
traverse reverse position shown in Figure 18. '
When the valve members are shifted to vthis posi
tion the hydraulic clutch actuating device 238 .
is automatically operated so as to disconnect the
work spindle 36 from the drive shaft 42, thereby
interrupting the actuation of the‘plunger- pumps.
Fluid from the low pressure gear pump I 58 is
then. directed from the .pipe I52~ through the 19
valve port I 54 ‘and into the passage I82. The
the opposite end of the cylinder is forced through
the action of the piston 68 through the pipe 238,
the check valve 232,. the pipe 234, and the pipe
248 into the rear extremity of the cylinder 88,
10 thereby causing the forward movement of the
piston 88. That is to say, the rapid approach
vof the rear tool carriage is effected by the rapid lateral'passage 226 of 'thevalve member I62-di
approach of the'front carriage actuator. By rects a portion of this ?uid through the valve
having the proper relationship in size of the port 2I6,_ and thence ‘outwardly through a pipe
bores in the cylinders 58 and 88, any predeter
line 218 which is connected to the left end of 1'5
thevcylinder 18 through the pipe 268, Figure 16.
mined movement of the piston 88 may be ob
tained by a corresponding movement of the This causes rapid reverse movement of the pis
piston 68. In other words, if the cylinder‘ bores’ ton 12, and fluid from‘the advancing side of the
are equal in size, the movement imparted to the piston is returned to the valve mechanism
20 piston 98 will be equal to .the movement :ex I through a section of the pipe line 258, the pipe 20
perienced by the piston 68. However, if the cyl
268, and the pipe 228, said latter pipe connect
inder bore 88 is larger in diameter than the bore 2 ing with the valve port 2I4. At this instant the
of the cylinder 58, the degree of movement of valve port 2l4 communicates with the lowipres- ,
the piston 98 will be less than the movement of sure chamber 2840f the valve mechanism, Fig-a .
- the piston 68. Thus, it will be apparent that by
employing the teachings of my invention the‘
degree of movement of one piston may be very
tion of the ?uid from the passage I92 is con
ducted by a lateral port or passage 212 to the
accurately controlled by the movement of van
valve port 2I2 which connects with the pipe 242.
other
30
ure 18. At the same instant the remaining por- . 25
piston.
-
1
‘
'
~
In machines heretofore ‘equipped with a plu
rality of actuators, the problem of accurately
controlling the movement of these actuators has
presented itself. In such conventional machines
it requires very accurate adjustment between
35 each actuator to enable the starting of cutting
tools simultaneously.
In my above mentioned
_ co-pending applications I have disclosed a needle
valve ‘arrangement for controlling the load be
tween the actuators, and it will be observed that
40 by providing .the. circuit ‘shown in the present
application I do not depend on this needle valve
arrangement for controlling both of the actua
tors 56 and 86 during the rapid approach move
ment. This is due to the fact that the actuator
45 .86 is operable directly. in‘ response to the opera
Low pressure ?uid is thus introduced within the
rear carriage cylinder 88 so as to impart rapid‘ 30
reverse movement to the piston 98. Fluid from
the advancing side of the piston 88 passes
through the pipe 248, the actuator 238, and
thence through a pipe-214 which connects with
,the valve port 2I8. This valve port- 2I8 like 35
the valve port 2I4 is connected with its com;
panion low pressure chamber 288.
'
‘Attention is directed to the action which takes
place at the instant the control valve is shifted
to its‘ rapid reverse position. At this time both 40
the rear and front tools are operatively engaging
the work piece. Due‘to the fact that the front
carriage iscmounted'upon the oscillatory bar 48,
the weight of the carriage will cooperate to re
duce the power necessary to swing the tool 54 v45
out of engagement with the work piece the in
tion of the actuator 56.
’
As just described, the shifting of the valves stant that the control valve is thrown into re
‘I68 and I62 to the left causes the simultaneous‘ verse. In other words, the mechanical arrange
rapid traverse of the tools 54 and 82 toward the ment of the front carriage is such as to set up
less resistance to reverse ?uid action than- the 50
50 work piece. The hydraulic clutch actuating
mechanism_ 238 which 'is connected-with the
rear carriage.
pipes 234 and 248 is also actuated during this
interval. The piston 258 thereof is urged to the
chanical had placed on the rear tool slide as a
left, Figure‘16, thereby connecting the main rear,
:w LI
drive shaft 42 with the work spindle 36. The
actuation of the hydraulic mechanism 238 may be
The rear tool, due to the me‘
result of the connection which it makes with the
automatic control slide, later to be described, and
due to the fact that it is horizontally slidable .55
will remain in contact with the work piece'long
timed so that‘ the work spindle 36 begins to ro-. < enough to complete its cut and will not return
tate and thereby actuates the plunger pumps, 84
until the rotation of the work spindle has been
-'completely arrested. It will be noted that the
riag'es ‘reach thellimit of their rapid traverse work spindle in the disclosed lathe rotates in a 60
direction which is opposite to the rotation of spin
movement toward the'work piece. At this in
.dles in conventional types of lathes.
stant the valve members I68 and I62 are re
turned to the neutral position ’shown in Figure
Automatic control mechanism
16, and the rotary valve 262 is shifted so as to
I shall-now proceed to describe the means for 65.
establish communication between the pipes 268
and 264. It will then be apparent that the automatically controlling the actuation of the
‘plunger pumps 94 and 94a deliverh?uid at high valve members I68 and I62, as well as the rotary
and 84a just as thefront and rear tool car
, pressure to the actuators 68 and 86. Under these
conditions the pump ' 94 is connected‘within a
closed circuit which includes the pipe I38, the
actuator 86, and the pipe I24, while the pump 94a
valve member 262.
This mechanism includes a
slide 216, Figures! to 4 inclusive, which is shift-v
able along the upper surface of the machine base 70
38 at ‘the front side of the machine. A rack 218
' is included within a closed circuit which includes. ' secured to the underside of the slide 216 is driven
the. pipe 258, the actuator 68, the pipe 268, and
'
'
.
thepipe 264.
When the tool carriages reach the limit of
from a pinion ,288 mounted upon' a shaft 282.
This shaft carries a bevel gear 284 at its opposite
extremity which meshes with a companion ‘gear 75
6
_ 2,078,698
288 on a shaft 288. 'Rotation is imparted to this
shaft 288 through the agency of a gear 280 which
meshes with a rack bar 292 secured to the under
movement to the right the head 3I2 is engaged
by the valve member I60, thereby causing said
head'to again close communication between the
side of the rear carriage slide 18, Figure 3. Thus, chamber 3| 6 and the reservoir.
5 when the rear tool carriage is reciprocated to
The sudden automatic reversal of the valve
ward and away from the work piece, movement members causes ?uid ‘to be urged in a reverse di
is imparted to the slide 216. This slide carries a ' rection‘ to the actuators 68 and 86 as above de
plurality of dogs 294, 296, 208, 300, and 302. In scribed, thereby imparting a rapid reverse move
the drawings the slide 216 is disclosed in the pc
ment thereto. As the slide 216 moves to the left,
110 sition which it occupies when the valve members the dog 296 eventually engages the ?nger I88, 10
‘I60 and I62 are in ‘neutral position. The shifting Figures 2 and 4, thereby causing the‘ valves I60
of the valve members I60 and I62 to the left is and I62 to be shifted to neutral position. This
occasioned by moving vthe control handle I58 to
the right, Figures-1 and 2. This imparts a clock
15 wise movement to the shaft I18, Figure 4, thereby
causing the ?nger I86 to be swung downwardly.
The shifting of the valve members to this rapid
approach position causes the forward movement
of the rear tool slide 18, as above set forth, and
20 the actuation of this slide causes the slide 216
to be urged to the right, Figures 2 and 4. The
dog 288 is so positioned von the slide that when
it reaches the ?nger I86, the lathe tools will have
been moved to their work engaging ppsition in
shifting of the valve members takes place when
the tool carriages have reached their initial or
starting position. During the shifting of the slide 15
216 to the left, the dog 300 is also moved into _
engagement with a ?nger 324 of the valve mecha
nism 262, thereby automatically shifting said
valveto the position shown in Figure 5. In this
position communication is interrupted between
the pipes 260 and 264, Figure 16, thereby render
-20
ing the closed circuit, including the plunger pump
94a, functionally inoperative until a se'cond cycle
of operation takes place, at which time the dog
302 causes‘the shifting of the valve 262 as above 25
25 readiness to perform a cutting operation upon the
work piece. The engagement of the dog 298 with ‘ described. In order to more positively assure the
the ?nger I86 causes the valve members I60 ‘and proper positioning of the valve member 262, I pro
I62 to be shifted to the neutral position shown
in Figure 16. Simultaneously with the actuation
30 of the valve members I60 and I62, or at any other
desired interval, the dog 302 is carried into en
gagement with a ?nger 304v which is carried upon
a shaft 306 extending inwardly from and secured
to the rotary valve 262, Figures 4 and 5. This
35 causes the valve 262 to be shifted from the posi
tion shown in Figure 5 in a counter-clockwise
direction so as to establish communication be
tween the pipes Y280 and 264 through a valve
passage 262a. The shifting of the valve 262 ren
vide a spring pressed plunger 262b, Figure 5,
which is designed to co-operate with companion
30
notches formed in the valve member 262.
Modi?ed valve
Referring to Figures 19. to 24 inclusive, it will
be seen that I have disclosed a modi?ed valve
construction, which is indicated generally by the
numeral I56a. This mechanism I56a includes
a valve. casing‘ 326, which slidably houses a single
valve member 328. When this valve member 328 _
occupies the neutral position shown in Figures
tiersv theclosed circuit, which includes the pump. 20 and 21,-?uid from the low pressure pipeline
84a, functionally operative so as to e?'ect the
feeding movement of the piston 12 to the left,
Figure 16. Thus it will be apparent that the dog
802 may be adjustably located upon the slide ‘216
so as to cause the actuation of the valve 262 at
any desired interval of the cycle of operation.
The longitudinal feeding movement of the tool
54, as well as the transverse feeding of the tool
82, continues until the dog 294 carried at the ad
50 vancing extremity of the slide 216 is moved into
40
I52 passes through 'an annular valve port 330
and thence through radial ports 332, which com
municate at their inner extremity with a central »
valve passage 334.
The left end of this valve
passage 334 communicates with a valve chamber
336, which communicates with the reservoir I46
through the pipe 206 in the manner previously
described in connection with the valve mecha
I56.
Thus,'?uid circulates through the
' nism
engagement with the free extremity of a pivoted ' valve mechanism I58a when the valve member
328 occupies the position shown. However, when ‘
?nger or lever 308 of the balancing mechanism
I 12. The inner extremity of the ?nger 308 is
. plvotaily connected to a shank 3I0, which is pro
vided with a head 3I2 at its inner extremity.
55 This head an is provided with longitudinalgpas
sageways 3“, and when said head occupies the
position shown in Figure 8, it serves to close com
munication between a valve chamber 3I6 and an
‘annular port 3I8.‘ This annular port_3l8 has
an unrestricted connection with the reservoir I46
through a passageway320, Figure 7, and a pipe
322, Figures 7 and 16. The engagement of the
dog 294 with the finger 308 causes the head 3I2
the valve member is shifted to the left (rapid ap
proach position) in the manner described in con
nection with the valve mechanism I 56, communi
cation is interrupted between the radial ports 332
and the annular port 330. In this position the
annular port 330 communicates with a lateral
valve port 338, Figure 21, which ‘communicates
with a port 2I4a which corresponds to the port
2I4 of the valve I56. This port 2 I40. may‘ be con 60
nected with the actuator 56 by the pipe 228. It
will be noted that in this shifted position of the I
valve member 328, a valve port 2I0a, which cor
to be shifted to the position shown in Figure l1,v responds to the port 2I0 of the valve mechanism
65 thereby uncovering the annular port 3 I 8 and thus , I56, is closed by a section 2I8a of the valve. In
this‘rapid approach position a return valve port
connecting the chamber 3I6, as wall as a cor
responding valvechamber 3I6a, with the reser
2I2a, which corresponds to the port 2I2, permits
voir I46. This causes an unbalancing of the ?uid
the return of ?uid from the pipe 242, which is
directed through the longitudinal valve passage
pressures upon the valve members I60 and I62
due to the fact that- the ?uid from the valve
chambers 3I6 and 3I6a is now free to ?ow back
to the reservoir I46. The pressure at the oppo
site extremities of the valve members causes the
Same to be automatically urged vgto the right, to
75 the position shown in Figure 18. During this
334.
.
70
'
When the valve member 328 is automat
ically shifted to its rapid reverse position,'
said valve serves to permit the discharge
of
2I2a.
low > pressure
and
2I6a
?uid
and
through
the
return
the
ports
of
?uid
,
2,078,696
7
through‘the ports 210a and 2H0. Thus, the sin
gle valve mechanism l56a corresponds in func
tional characteristics to the double valve mech
anism I56 in that the rapid approach position of
sity of employing auxiliary mechanisms. Fur
said mechanisms causes low pressure ?uid from a
single source of supply to be directed through a
tem, wherein ?uid from a single ‘source of sup—
ply is directed through a single valve to a single
actuator, which actuator causes the movement of
single valve port to a ?uid actuator, which ac
tuator in turn controls the functioning of a second
actuator. Also, when said mechanisms occupy
10 their rapid reverse position, ?uid from said sin
gle source of supply is received through a pin
rality of ports and directed to a plurality of ac
tuators for the purpose of rapidly shifting said ac
tuators. One of the advantages‘ resulting from
the use of the double type valve mechanism I56
resides in the fact that any variation in pressure
of the circuit controlled by one of the valve mem—
vbers will not affect the other valve member. It
should be noted that the valve mechanism I 56a. is
20 connected with two independent. feeding cir
cuits, while in the double type mechanism I56,
the valve member Hill is connected with one of
the circuits, and the ‘valve member I62 is inde
thermore, it is only necessary to employ a single
source of fluid supply. It will be apparent that
my invention provides a hydraulic actuator sys
_a second actuator.
It will also be seen that the A
second actuator is connected with a control mech
anism which timingly regulates the starting and 10
stopping, as well as the speed of operation of both
of said actuators. The type of control _valve
which I have described, presents a marked im
provement over types which have been employed
heretofore, in that the mechanism is self-con
tained. All of the shiftable parts are housed
within a single casing, and the mechanisms for
imparting movement thereto, namely, the shaft
I18 and associated parts, Figure 6, are mounted
within one extremity of the casing. The valve 20
members are simple in construction and hence
may be economically produced.
I
v
I have shown the pistons of the various ac
pendently connected with another circuit.
Check valve
Particular attention is directedlto the struc-_
ture of thecheck valve 232, Figures 15 and 16.‘
This valve includes a casing 340, one extremity of
30 which is connected to the pipe 230 and the other
to the pipe 236. ‘A sleeve 342 is secured against
longitudinal displacement within the casing 340
tuators equipped with piston rods which extend
on both sides thereof, ,so that equal volumes of‘
?uid will be taken into and discharged from
- v by means of a key 3%, and longitudinally slidable
construction shown in Fig. 16, I present a closed
circuit arrangement whereby the same volume of
within the sleeve 342 is a plunger 366.
This
plunger is urged downwardly within the casing‘
340 through the action of a coil spring 348 which
is interposed between the plunger-‘and a remov
able cap or plug 360. A central passageway 352
> in the plunger receives ?uid from the pipe 233,
40 and this ?uid is directed into radial ports 355. If
the ?uid from the pipe 230 is of su?icient pres
sure to overcome the action of the spring 348, the
opposite sides of the pistons.
Obviously this
speci?c piston and piston rod construction is not
necessary in instances where suitable vents or
bleed passages are employed, such as those dis- '
closed in one of my above mentioned co-pend
ing applications. However, by using the type of
?uid discharged by the high pressure pump to one
side‘of the actuator piston, is received by said
pump from the opposite side of said piston. In
other words, the volume of ?uid discharged from
the advancing side of the actuator piston is
just su?lcient to charge the plunger pump. In
view of the fact that I employ the type of plung
er pump shown in detail in Figures 12 and 13,
it is possible to eliminate the use of relief valves
radial ports 35% thereof are carried into com
across the closed circuits. If an actuator pis
munication with an annular passage 358, ?uid
ton; as for example, the piston 90 is suddenly
from said annular passage 358 will ?ow into the.-- interrupted in its movement, the plunger pump
pipe 23%. This check valveis of improved prac
94 is rendered functionally inoperative until the
tical construction and is particularly adaptable obstacle which causes the interruption of the
for use in connection with the ?uid circuit de'piston movement, is removed. In other words.
scribed above. The check valve differs from the if the advancing end of the piston 90 is carried
common forms of check. valve in that a certain. into contact with either end of the pylinder 88
movement of the plunger thereof must take place and the spindle 35 continues to rotate. the sud
before ?uid will be directed from the pipe 230, to den engagement of the piston‘will automatically
the pipe 23$. It will also be observed that my im
render the pump 94 functionally inoperative.
proved check valve is completely sealed‘ against That is to say. the rotary mechanism within the
leakage.
‘
pump will actuate without e?ecting reciproca
plunger 366 will be urged upwardly, and when
Summary
From the foregoing it will be apparent that
my invention ‘contemplates the provision of a
metal working machine and a hydraulic actuator
system in .combination therewith, which is of
improved practical design. Practical tests have
shown that my improved circuit arrangement
enables a plurality of machine tools to be very
accurately and positively controlled. In'the ?rst
place, by having one actuator directly respon
sive to‘ another actuator, both of said actuators
will begin movement simultaneously regardless
of the load on the carriages. In the second place,
the degree and speed of movement of these car
' riages are accurately controlled.‘ In fact, the
starting of the cutting action of a plurality of
tools can be controlled with extreme accuracy,
and these results are obtained without the neces
tion of the pump pistons.
_
.
It should also be noted in connection with mv
improved type of check valve, that it differs
from conventional construction. in that, when
pressure on the opposite sides of my valve is
neutralized, the plunger of the valve will ex
perience no movement, due to the fact that the
spring is urging said plunger against the valve
seating.
_
In conventional types of check valves, when.
the pressure on the opposite sides thereof, is
equalized, said valves will not prevent thev ?ow
of ?uid therethrough.
However, in my inven- -
tion, the flow of ?uid from one side of the valve
to the other, is positively prevented when the
?uid pressure on the opposite sides thereof, is
neutralized.
-
-
By having the rear carriage It coupled with 76
i8
2,078,696
the dog carrying slide 216 through the agency of
the rack 292,-gear 280, shafts 288, 282, 'etc., said
actuators, and control mechanism for timingly
rear carriage is under a greater load during
governing the direction and extent‘ of movement
of said actuators with respect to each other.
reversal than the front carriage 46. In other
words, the front carriage 46 merely reverses along
of ?uid operated actuators, ?uid propelling
the bar’ ‘8 with very little frictional resistance
to overcome whereas the rear carriage not only
experiences the-friction set up by the engage
ment of the slide or carriage 18 on the guide
frame 80, but all the resistance or load which is
established by the v‘mechanism which connects
the slide 216 with the rear carriage. With such
4. In a hydraulic actuator system, a plurality '
a:
means for supplying ?uid under pressure to one
of said actuators, means for conducting ?uid
from said last mentioned actuator to a second
actuator, whereby the movement of the ?rst ac
tuator will effect the actuation of the second 10
actuator, thereby causing the speed and start
ing of said second actuator to ‘be accurately gov
a construction, it will be apparent that under ?uid - erned by ?uid displaced from the advancing side
pressure the front carriage will reach its start-v of the ?rst actuator, means for controlling the
ing position before the rear carriage. In this effective connection .of the ?uid propelling means
with said ?rst mentioned actuator, and means
way I am able to‘accurately control the func
tioning of the control valve by the carriage operatively coupling said control means with one
of said actuators whereby said control means is
which is normally under the greatest load dur
governed in response to the actuation of one .of
ing reversal, a condition which is most advan
tageous in using hydraulic circuits of the type
described and claimed herein. Attention is'also
said actuators.
,
20
5. In a hydraulic actuator system, a plurality
directed to the fact that in my machine the
of ?uid operated actuators, ?uid propelling
reservoir I46 .is always positioned above the
means for supplying ?uid under pressure to one
hydraulic actuators so as to preclude the en
of ,said actuators, means for conducting ?uid
trance of air within the system.
While I, have disclosed my invention as applied
to an automatic lathe construction, it should be
understood that said invention is by no means
from said last mentioned actuator to a second 25
accurately control the shifting of a'plurality of
actuators. Therefore my invention should be
limited only by‘ the scope of the appended claims.
operatively connecting said valve mechanism
with one of said actuators whereby said valve
actuator, whereby the movement of the ?rst ac
tuator will effect the actuation of the second
actuator, a shiftabie valve mechanism for con
limited to such devices, but is capable of being . trolling the connection of, the ?uid propelling
means with said ?rst actuator, and means ‘for 30
30 used in any instance where it is desirable to
Having, thus described my invention, what I
claim as‘new and desire to secure by Letters
‘Patent is:
1. In a hydraulic actuator system, a plurality
of ?uid operated actuators connectable with ma
chine parts and the like, means for supplying
40 ?uid under pressure to one of said actuators for‘
imparting movement thereto, means connecting
.said last mentioned actuator with a second ac
tuator, whereby said ?rst actuator serves to con
~ trol the operation of said second actuator and
, thereby effect simultaneous action of said ac
_ tuators irrespective of the resistance experienced
by said actuators, and control mechanism for
timingly governing the direction and‘extent of
movement of said actuators with respect to each
other.
.
Y
,
.
2. In a hydraulic actuator system, a plurality
of ?uid operated actuators, each of said ac
mechanism is shiftable in response to the actua- ,
tion of one of said actuators.
6. In combination, with a plurality of shiftabie
tool carrying devices, a ?uid operated actuator
associated with each of said tool carrying de
vices, means for delivering ?uid under pressure
to the actuator associated with one of said tool
carrying devices, a duct connecting said last.
mentioned actuator with the actuator of a sec
v40
ond tool carrying device, whereby the speed of
travel of said second tool carrying device is con
trolled in accordance with the displacement of
?uid from the advancing side of the actuator
associated with said ?rst tool carrying device
tov thereby accurately govern the degree of
movement of said second actuator, and ?uid
control means associated with one of "said ac
tuators whereby to initiate a change in the rate
of ?uid delivery after a predetermined amount 50
of ?uid has been displaced from the advancing
tuators including a cylinder and a piston recip- -_ side of the ?rst actuator.
‘rocable therein, means for ‘supplying ?uid under
pressure to one of said ‘actuators for effecting
the shifting thereof, a duct connecting said last
' mentioned
actuator
with a second actuator,
v
7. In a hydraulic system of ' control, a pump,
a shiftable valve having a plurality of inlet and
outlet ports, ‘a plurality of ?uid operated ac
tuators, ducts connecting said shiftabie valve
with said actuators, said valve being adapted in
whereby ?uid may be forced from said ?rst ac
one shifted position to receive ?uid from said
tuator to eifect' the shifting of said second ac
pump, direct said ?uid to one of said actuators,
60 tuator, and control means for receiving ?uid ‘and to receive ?uid from a second of said ac
from said ?uid supplying means and directing tuators, said valve being shiftabie in timed rela 60
said ?uid to at least one of said actuators in tion with the movement of one of said actuators
accordance with the desired direction of move
and a duct connecting said ?rst actuator with
ment with respect to each other.
said second actuator, whereby said ?rst actuator
3‘. In combination with a plurality’ of shiftabie is adapted to hydraulically control said second
machine elements, a ?uid operated actuator for actuator.
_
each of said ‘elements, means for supplying ?uid
8. In a hydraulic system of control, a plurality
under pressure to one of said actuators to ef-‘ of ?uid operated actuators, means for supplying
vfect the movement of the machine element as
?uid under pressure,’ a valve mechanism con
sociated therewith, a duct for directing ?uid nected with said ?uid supplying means, said 70
from said last mentioned actuator to a second valve mechanism having a plurality of ports
actuator, whereby said ?rst actuator will control and shiftabie to at least two positions in timed
the actuation of said second actuator and there
relation with the movement of one .of said ac
by eifect simultaneous action of said actuators tuators ducts connecting said ,valve‘iwith said
irrespective of the resistance experienced by said actuators, said valve in one shifted position be-'_ 75
7
9
2,078,696
‘ing adapted to direct ?uid from said supplying
?uid conducting means for effecting the start
ing and speed of a second of said actuators in re
another actuator, and connecting means for' sponse to the actuation of said first mentioned
rendering said last mentioned actuator operable actuator, and means operable in ‘response to the
actuation of said second actuator for controlling
in response to the actuation of said ?rst men
‘the actuation of said valve.
14. In combination with a plurality of shift-'
,9. In a hydraulic system of control, a plurality
of ?uid operated actuators, means for supplying able tool carrying devices, a ?uid operated actu
ator associated with each ‘(if said tool carryingv
?uid under pressure, a valve mechanism connect
devices, a pump for supplying ?uid under pres 10
ed,
with
said
?uid
supplying
means,
said
valve
10
being shiftable to at least three positionsand , sure, a valve for controlling the delivery of said
having a plurality of outlet and inlet ports, ducts ?uid under pressure to one of said actuators, ,
connecting said valve with ‘said actuators, said ?uid conducting means for effecting the start
valve in one position, interrupting communication _ ing and speed of a second of said actuators in
15
15 between the supplying means andsaid actuators, response to the actuation of said ?rst mentioned
‘and in a second'shiftable position adapted to actuator, and a member shiftable in response to
means to one actuator and to receive ?uid from
tionedv actuator.
,
'
n
,
_
.
1
supply ?uid to one of said actuators-and receive
the actuation of one of said actuators for con
trolling the actuation of said valve.
15. In a hydraulic actuator system, a plurality
of ?uid operated actuators, a machine element 20
connected to each of said actuators and shifted
said ?rst actuator, said valve .in a third shiftedv thereby, pump means for supplying ?uid under
position ‘being adapted to deliver and receive pressure, a valve for directing ?uid under pres
sure to one of said actuators, a duct connect
?uid from a plurality of said actuators.
10. In combination with a hydraulic actuator ing, said last mentioned actuator with a second 25
25
system, including a plurality of ?uid operated actuator, whereby the speed of said second actu
ator is controlled by the ?uid displaced from said
actuators, means for supplying ?uid under pres
first actuator, rotary work carrying means, driv
sure, and a reservoir, a valve mechanism includ
ing means therefor, and means operable in re- .
ing a valve member shiftable to at least two posi
sponse to one of said actuators for controlling 30
30 tions, a port in said valve mechanism which is
adapted, when the valvev member is shifted to the connection between the work carrying means
one position, to direct ?uid under pressure to and said driving means.
16. In a hydraulic actuator system, a plurality
one of said actuators, and a second port for con
. temporaneously receiving ?uid from‘ another of of ?uid operated actuators, a machine element
said actuators and, for directing said ?uid to driven by each actuator, a single pumping mech 35
anism for supplying ?uid under pressure, a uni
said reservoir, said valve being adapted in an
tary valve mechanism for directing ?uid under
other shifted position to direct ?uid under pres
sure to a plurality of said actuators and to receive pressure to one of said actuators, means connect
ing said actuator with a second actuator, where
?uid from said actuators.
by to control the starting and speed of said 40
40' 11.~In combination with a hydraulic actuator
system, including a ‘plurality of ?uid operated second actuator, and means operated in timed
relation with one of said actuators for control
actuators, a pumping ‘means, and a ?uid reser
voir, ‘a valve mechanism having a valve member ling the actuationrof said unitary valve mech
anism.
shift‘able to various positions and ‘having a plu
?uid from another of said actuators, and a duct
connecting said ?rst‘ actuator and said second
20 actuator, wherebymo‘vement of said second actu
ator is occasioned in response to movement of
rality of inlet and outlet ports connectable with
said actuators, said-valve ‘in one shifted position
being adapted to receive ?uid from saidpump
, and dispatch said ?uid to the reservoir, and in
a second position to. dispatch ?uid under ‘pres
sure to'a single’ actuator and receive ?uidfrom
another single actuator, and in a third position
to dispatch ?uid to a plurality of actuators and
receive ?uid froma plurality of actuators.‘ '
12. In combination with a hydraulic actuator
- system, including a?plurality- of ?uid operated‘
a actuators,‘ a, pump for supplying ?uid under pres-
» sure, and a reservoir,_a valve mechanism includ
' (ing a-plurality of_~valve.members shiftable with- »
1 vin a casing,vsa_id mechanism being hydraulically
connectable with the pump and said actuators,
60
,
17. In combination with a plurality of shift
able tool carriages, a ?uid operated actuator con
nected with each tool carriage, a single source‘ of .
?uid pressure supply effectively connectable with
one of said actuators, a second of said actuators
being connected with and operated by said last _mentioned actuator, and means operated by one
of said actuators for controlling the delivery of
?uid from said single source of supply to another
actuator.
.
_
18. In a materiaLworking apparatus of the class
described, a plurality of shiftable machine ele-,
ments, a ?uid operated actuator connected with
each element, a constantly drivenlarge displace
ment pumping mechanism for supplying ?uid
under pressure, a valve mechanism for controlling 60
one of said‘ valve members being adapted in one - the-delivery of ?uid from said constantly driven
- shifted position-to direct ?uid under pressure to pumping mechanism to a ?rst of said actuators,
a single actuator, and the other valve member a duct connecting said last mentioned actuator
being adapted the same instant, to receive’ ?uid with- a second actuator, whereby the second actu
65 from another actuator, said valve members in. ator is driven by said ?rst actuator, and a high
pressure ?uid propelling means connectable with
av second shifted position being adapted to dis
patch ?uid under' pressure to a plurality of 'said ‘ one of said actuators for propelling said actuators
.
actuators and'to receive fluid from a plurality at different'speed.
19. In a hydraulic actuator system, a plurality
of said actuators.
.
‘
'
13. In combination with a plurality of shift-» of ?uid operated actuators connectable with ma 70
chine parts and the like, means for supplying ?uid
able tool carrying devices. a ?uid operated actu
ator associated with each of said tool carrying under pressure to a ?rst of said actuators for im
parting movement thereto, means connecting said
devices, a pump, for supplying ?uid under pres
sure, a valve for controlling thedelivery of'said last mentioned actuator with a second of said
75 ?uid under pressure to a first of said actuators,
actuators, whereby said ?rst actuator serves to
2,078,696
control the operation of said second actuator
and travels simultaneously with said second actu
ator, means connecting said ?uid supplying means
with another of said actuators, and control mech
anism for timingly governing the direction and
extent of movement of said actuators.
20. In combination with a plurality of shiftable
machine elements, a ?uid operated actuator for
each element including a piston within a cylinder,
10 means for supplying ?uid under pressure to one
side of the piston vin one of said actuators to effect
the movement thereof in a given direction, a duct
described, a tool supporting means, a bar providing
an oscillatory support for said tool supporting
means and adapted to reciprocate said tool sup- .
porting means longitudinally, a hydraulic actu
ator for effecting the oscillation of said tool sup
porting means, a second shiftable tool supporting
means, a ?uid operated actuator connected there~
with, said last mentioned actuator being hy—
draulically connected and driven by said ?rst
mentioned actuator, and a source of ?uid supply
connectable with said ?rst mentioned actuator.
25. In -a hydraulic actuator system, a ?uid op
erated actuator including a piston within a cylin
for directing ?uid from the discharge side of said
piston to the cylinder of a second actuator, where
der, a conduit having one end connected with one
15 by the movement of said second actuator will be _ side of said cylinder, a pumping mechanism hav 15
controlled in response to the movement experi
ing the intake side connected with the opposite
enced by said ?rst mentioned actuator, ?uid con
end of said conduit, and a second conduit ex
ducting means connecting said ?uid supplying tending from the discharge side of said pumping
means with another of said ?uid operated actu
mechanism to the other side of said cylinder,
20 ator, and control mechanism for timingly gov
the ?uid discharged by one side of the piston be
erning the direction and extent of movement of ing equal in volume to the ?uid received on the
said actuators.
opposite side of said piston and being sufficient to
21. In a hydraulic actuator system, large deliv charge said pumping mechanism.
ery pumping means for supplying ?uid under low
26. In a hydraulic actuator system, a ?uid .oper
" pressure, a ?uid operated actuator, a valve mech
anism for controlling the effective connection
between said pumping mechanism and said actu
ator, a second ?uid operated actuator, a duct con- -
necting said ?rst actuator with said second actu
ator, whereby the movement of said second actu
ator is controlled in response to the movement of
the ?rst actuator, a third actuator connectable
with said source of low pressure ?uid supply, a
high pressure pumping mechanism connected
" with said second ?uid operated actuator and av
high pressure pumping mechanism connected
with said third ?uid operated actuator, the low
pressure ?uid serving to impart rapid traverse
- to said actuators, and the high pressure ?uid
40 serving to' impart feeding movement to said
actuators.
22. In material working apparatus of the class
described, a plurality of ?uid operated actuators,
machine elements connected with said actuators
45 and driven thereby, a single source of_ low pres
sure large displacement ?uid supply, a valve
mechanism for controlling the delivery of ?uid
ated actuator including a piston within a cylinder, '
a conduit having one end connected with one side
of said cylinder, a variable displacement pumping
mechanism having the intake side connected with
the opposite end of said conduit, and a second
conduit extending from the discharge side of 30
said variable displacement pumping mechanism
to the other side of said cylinder,_ the ?uid dis
charged by one side of the piston being equal in
volume to the ?uid received on the opposite side
of said piston and, being su?icient to charge said 35
variable displacement pumping mechanism.
'
. 27. In a hydraulic actuator system, a ?uid op
erated actuator including a cylinder, a piston
therein, said piston having a piston rod section
of equal size extending on opposite sides thereof, 40
whereby ?uid taken into one side of the cylinder
will be equal in volume to the ?uid discharged '
from the opposite side of said cylinder, a duct con
nected at one end to one side of said cylinder,
a variable displacement pump having its intake
side connected tov the opposite end of said duct,
anda second duct extending from the discharge
side of said variabledisplacement pump to the
other side of said cylinder, the ?uid discharged
50 second actuator, whereby ?uid from the ?rst
from the side of the actuator being su?icient to
actuator may be forced toward the second actu
charge said plunger, pump.
ator for shifting same, a high pressure ?uid dis- '
28. In a material working apparatus of the
placing means connected with said second actu
ator, driving means for said high pressure ?uid class described, a shiftable machine element, a
?uid operated actuator for shifting said element,
55 displacing means, and means for controlling the
connection between said driving means and said said actuator including a piston within a cylin
high pressure displacing means, said controlling der, the volume of ?uid adapted to be taken into
means operating to disconnect the driving means one side of said cylinder being equal to the
during the displacement of the low pressure ?uid amount capable of being discharged at the oppo
site side of said cylinder, a duct connected at one
60 to said actuators.
from said source of supply to one of said actu
ators, means connecting said actuator with a
. 23. In material working‘ apparatus of the class
described, a machine frame, rotary supporting
means, an oscillatory and reciprocable tool sup
port, a second reciprocable tool support, a ?uid
operated actuator connected with each tool sup
port, means for supplying ?uid under pressure
to one of said actuators, means connecting said
last mentioned actuator with the second actuator,
whereby the movement of the second actuator
70 is controlled by said ?rst actuator, and means
operable by the tool support associated with one
of said actuators for controlling the connection
between the source of ?uid supply and said ?rst
actuator.
75
'
.
24. In material working apparatus of the class
end to one side of said cylinder, a variable dis
placement pump having its intake side connect
ed to the opposite end of said duct, and a second
duct extending from the discharge side of said
pump to the other side of said cylinder, whereby
?uid from the discharge side of said actuator
serves as the sole charging ?uid for said
displacement pump.
variable 7
_
29. In a hydraulic actuator system, a ?uid op
erated actuator including a cylinder and a piston
within said‘ cylinder, a variable displacement 70
pump, a closed duct connecting one side of said
cylinder with the intake side of, said pump, a
closed duct "connecting the discharge side of said
pump with the other side of said cylinder, where
11
2,078,696
by to present av closed ?uid circuit, and a second
?uid operated actuator connectable in series with
the ?rst mentioned actuator.
_
to said actuators, a member mechanism driven by
one of said actuators, means on/said member for
timingly controlling the actuation of said valve
means for supplying ?uid under pressure to one
mechanism, a second valve mechanism for inde
pendently controlling the ?uid in connection with
one of said actuators, and means on said member
for timingly actuating said second valve mech
of said actuators for effecting the shifting there
anism.
forced from said ?rst actuator to effect the shift
ing of said second‘ actuator, and a valve in said
duct to prevent the reversal of ?owof ?uidinto
mechanism for propelling one of said ‘actuators at
30._ In a hydraulic actuator system, a plurality
of ?uid operated actuators, each of said actua
tors including a cylinder and a piston therein,
~
36. In a hydraulic system for controlling a plu
of, a duct connecting said last mentioned actua- '.
10 tor with a second actuator, whereby ?uid may be rality of ?uid operated actuators, a ?uid pump 10
said ?rst mentioned actuator.
15
‘
.
31. In combination with a hydraulic circuit
including a plurality of hydraulic actuators for
a feeding rate, a second ?uid mechanism for pro
pelling another of said actuators at a feeding
rate, a third ?uid pumping mechanism for pro
pelling said actuators at rapid traverse speed, 15
a valve mechanism for selectively controlling the
propelling machine parts and the like, ?uid con-7 delivery of ?uid from said pumping mechanism to
said actuators, a member mechanism ‘driven by
ducting means connecting a pair of said actu
ators comprising a check valve including a cas
20' ing, means at one end of said casing for con
nection with said circuit, means at the ‘opposite
end of said casing for connection with said circuit,
and a shiftable member within said casing which
is adapted upon being shifted a predetermined
25 .amount to establish communication between the
opposite ends of said casing.
a)
32. In combination with a hydraulic circuit
one of ‘said actuators, means on said member for
timingly controlling the actuation of said valve
mechanism, a rotary valve mechanism for inde
pendently controlling the ?uid in connection with
one of said actuators, and means on said member
for timingly actuatingsaid rotary mechanism.
37. In a hydraulic valve mechanism for con
trolling the operation of a plurality of ?uid op
erated actuators, including a casing, a plurality
of shiftable valve members in said casing, ar
ranged in substantial parallelisms, and means for
‘connecting and disconnecting said valve members, 30
whereby to render the same operable independ
ently and also shiftable as a unit within said
including a plurality of hydraulic actuators for
propelling machine parts, and the like, ?uid con
30 ducting means connecting a pair of said actua
tors comprising a check valve including a casing,
means at one end of said casing for connection
with said circuit, means atv the opposite end of
i, said casing for connection withrsaid circuit, a ‘ ~ 38. A valve ‘mechanism for controlling the op
shiftable member within said casing which is eration of a plurality of ?uid operated actuators
adapted upon being shifted a predetermined including a casing, a valve member shiftable to at
amount to establish communication between the least two positions in said casing, a port in said
opposite ends of said casing, and resilient means valve mechanism adapted when the valve member
is shifted to one position, to direct ?uid to a
for urging said shiftable member in a givendirec
selected actuator, and a second port for con 40
40 tion.
,
'
33. In combination with a hydraulic circuit temporaneously receiving ?uid from another
including a plurality of hydraulic actuators for actuator, said valve having a plurality of ports
whereby when occupying another shifted posi
propelling machine parts and the like, ?uid con
ducting means connecting a pair of said actuators tion, said valve serves to contemporaneously di 45
rect ?uid to a plurality of said actuators and to
45 comprising a check valve mechanism including a
_ casing, a plunger within said casing, cooperative receive ?uid from said actuators.
: 39». A system of hydraulic control including a
ports adapted to establish communication be
plurality of hydraulic actuators, a relatively high
tween opposite ends of , the casing when said
pumping mechanism, a second lower
plunger has been shifted a predetermined amount, pressure
pressure pumping1 mechanism for propelling said _ 50
50 and resilient means for urging said plunger in'a
actuator at a relatively rapid rate, shiftable con—
. given direction.
,
trol mechanism adapted in one shifted position to
34. In combination with a hydraulic circuit direct ?uid from said high pressure pumping
including a plurality of hydraulic actuators for mechanism to one of said actuators independently
' propelling machine parts and the like, ?uid con
'of said second mentioned pumping mechanism,
}ducting means connecting a pair of said actua
and ?uid conducting means connecting a pair of
=tors comprising a check valve mechanism includ-, said actuators, whereby the movement of one
ing a casing having an intake'port at one end actuator is controlled by the ?uid displaced from
‘thereof and a discharge port at the other end the other actuator.v
thereof, a plunger reciprocable within said cas
40. A system of hydraulic control including a
ing, said plunger-having a longitudinal passage plurality of hydraulic actuators, a relatively high
and a radial port communicating therewith, and pressure feeding pump, a low pressure rapid
resilient means for urging said plunger toward traverse pump, control mechanism for render~
one extremity of said casing.
ing the rapid traverse pump functionally inop;
_ 35. In a hydraulic system for controlling a plu
erative for propelling purposes with respect to at 65
rality of fluid operated actuators, a ?uid pump least'one of said actuators during the function
mechanism for propelling one of said,actuators ing of the high pressure pump, and ?uid conduct
at- a feeding rate, a second ?uid pumping mecha
ing means extending between a pair of said actu
nism for propelling another of said actuators at ators, whereby the movement of one actuator is
a feeding rate, a third ?uid pumping mechanism controlled in accordance with the displacement
for propelling said actuators at rapid traverse of fluid from the other.
speed, one of said actuators being controlled di
41. In a hydraulic actuator system for moving
rectly in response to another of said actuators, machine parts and the like, a plurality'of hy
a‘valve mechanism for selectively controlling the draulic actuators connectable with said machine
delivery of ?uid from said pumping mechanism parts, each of said actuators including a piston
casing.
'
/
I
12
2,078,696 ‘
within a cylinder, ?uid propelling means for im
parting feeding movement to at least one of said
actuators, a second ?uid propelling means for
imparting rapid traverse movement to at least one
5 of said actuators, a valve for cutting off said sec
the actuators and in another shifted position to
render said propelling mechanism. functionall
inoperative for propelling purposes.
Within a cylinder, a feed pump, a rapid traverse
pump,. a ?uid reservoir connected with said
rapid traverse pump, and shiftable means in
cluding a plurality of .valve members shiftable 10
as a unit within a casing for controlling the
operative functioning of said pumps with respect
and ?uid conducting means extending between a
pair of said actuators, whereby the movement of
10 one actuator will control the movement of the
.otheractuator in accordance with the displace
_
42. In material working apparatus of the class
described, a prime mover, a hydraulic actuator in
l5 cluding a piston within a cylinder, ?uid propelling
mechanism driven in timed relation with said
to the actuators, said valve members being adapt
ed in one shifted position to direct ?uid dis
charged by said rapid traverse pump to the 15
reservoir independently of the ?uid discharged
prime mover and adapted to impart‘a linear speed
by the feed pump and in another shifted position
serving to deliver ?uid discharged by the rapid
to the actuator piston which is constantly pro
portional to the speed of travel of said prime
20 mover, means connecting said ?uid propelling -
mechanism with said hydraulic actuator, a second
hydraulic actuator including a piston within a
cylinder, and ?uid conducting means extending
between said actuators, whereby one actuator
25 serves as an impeller for the other actuator,
43. In material working apparatus of the class
‘described, a prime mover, a hydraulic actuator
'
ing machine parts and the like; a plurality of
hydraulic actuators each including a piston
ond mentioned propelling means during the op
erative functioning of the other propelling means,
ment of ?uid from one actuator to the other.
_
46. In a hydraulic actuator systemfor mov
traverse pump for rapid traverse purposes to said
actuators.
'
ing machine parts and the like, a plurality of.
hydraulic actuators each including a piston
within a cylinder; a feed pump, a rapid traverse
pump, a control device including a plurality of 25
valve members shiftable within a casing, said
valve members adapted to occupy one of at
including a piston within a cylinder, ?uid pro
pelling mechanism driven in timed relation with
least three positions, namely, a neutral position,
30 said prime mover and adapted to impart a linear
connecting said valve members with said rapid
traverse pump, said valve members being ‘adapt
ed in their neutral position to effect the circu
lation of ?uid from said rapid traverse pump
speed to the actuator piston which is constantly
proportional to the speed of travel of said prime
mover, means connecting said ?uid propelling
mechanism with said hydraulic actuator, means
35 for imparting rapid movement to said actuator,
a second hydraulic actuator including a piston
within a cylinder, and ?uid conducting means
extending between said actuators, whereby one
actuator serves as an impeller for the other
actuator.
_
44. In material working apparatus of the
class described, a frame, a spindle rotatably
mounted in said frame, a tool carriage shiftable
transversely of the spindle, a ?uid actuator for
moving said carriage, a variable displacement
pump driven from the spindle for propelling said
actuator, a second oscillatory carriage for mov-_
ing a tool toward and away from the‘axis of the
spindle and for moving said tool longitudinally
of said spindle, a ?uid actuator for longitudinally
shifting said second carriage, a second variable
displacement pump driven from said spindle for
moving said second actuator, a third ?uid oper
ated actuator for shifting said carriage toward
the spindle axis, means for imparting rapid
traverse to said actuators, and means for selec-,
tively controlling the operative functioning of
the variable displacement pumps and the means
for imparting rapid movement to said actuators.
60
20
'
4'7. In a hydraulic actuator system for mov
a forward position, and a reverse position/means
independently of the ?uid discharged by the
feed pump, the forward shifted position of said
valve members serving to operatively connect
said rapid traverse pump with said actuators ,
and the reverse shifted position of said valve
serving to direct ?uid in a reverse direction to
said actuators, and means for rendering the feed
pump. functionally inoperative during the oper
ative functioning of said rapid traverse pump.
48. In a hydraulic ,actuator system for con~
trolling the movement of machine parts and
the like, a plurality of hydraulic actuators each -
including a piston within a cylinder, a pumping
mechanism for supplying fluid under pressure,
a shiftable control valve for controlling the de
livery of ?uid from said pumping mechanism to
at least one of said actuators, and ?uid conduct- @
ing means extending between said actuators,
whereby ?uid may be delivered from one actu- '
ator to the other for controlling the movement
thereof, said conducting means including a
valve which is adapted when the control valve is
positioned to direct ?uid from said pump to at
least one of said actuators to
of ?uid through said connecting
direction and when said valve
cation between said pump and
permit the flow
means in a given
closes communi
said actuator to 60
45. In a hydraulic actuator system for con
trolling the movement of and ‘for actuating ma
prevent the ?ow of ?uid through said connect
chine‘ parts and the like, a plurality of hydraulic ' ing means in a reverse direction.
actuators, each including a piston within a cyl
49. In metal working apparatus, means for
inder, ?uid propelling mechanism for delivering
?uid under relatively high pressure for feeding
purposes, a second ?uid propelling mechanism
for delivering ?uid under lower pressure for
rapid ‘traverse purposes, a shiftable valve means
including a plurality of valve members shiftable
TO as a unit within a casing for selectively control
ling the delivery of ?uid‘ from the low pressure,
?uid propelling means for rapid traverse pur
poses to said actuators, said valve means serv
ing in one shifted position to operatively con
75 nect the low pressure propelling mechanism with
rotatably supportinga work piece, a tool carriage
shiftable toward and away from the work piece, 65
a second shiftable tool carriage, a hydraulic
actuator coupled with each carriage; a pump for
supplying ?uid to said hydraulic actuators, a
valve mechanism for controlling the delivery of
?uid from said pump to at least one of‘ said 70
actuators, and ?uid conducting means extending
between said hydraulic actuators, whereby the
hydraulic propulsion of one carriage causes a dis
v placement of ?uid to effect the movement of the
other carriage to thereby accurately control the
Cl
2,078,696
relative degree and rate of movement of said
carriages.
,50. In metal working apparatus, a rotatable
work support, a front carriage shiftable toward
and away from the work piece, a rear carriage
shiftable toward and away from the work piece,
a hydraulic actuator coupled with each of said
carriages for effecting'the movement thereof, a
pumping mechanism for supplying ?uid under
10 pressure,
,
13..
actuators, whereby the movement of one
carriage will be accurately timed with respect
to the other carriage when said-valve is posi
tioned to render the rapid traverse pump func
tionally operative, and means for preventing a
reversal of ?uid ?ow within said connecting
means when the feed pump is rendered function
ally operative.
_
55._ In material working apparatus, a rotatable
a valve mechanism for controlling
work support, a front carriage shiftable toward 10
and away from and longitudinally of 'the work
said pump to said actuators, and ?uid conducting _ piece, a rear carriage shiftable toward and away
means extending between said hydraulic actua
from the work piece, a hydraulic actuator for
tors, whereby the actuator of one carriage serves shifting the carriage toward the work piece, a
15. as an impeller for the actuator of the other second hydraulic actuator for moving said 15
carriage.
~
carriage longitudinally of the work piece, a third
51. In metal working apparatus, a rotatable hydraulic actuator for shifting the rear carriage,
work support, a front carriage shiftable toward ,7 pumping means for imparting feeding movement
and away from and longitudinally of the work to the second and third hydraulic actuators, a
20 piece, a rear carriage shiftable toward and away rapid traverse pump, a valve mechanism for 20
from the work piece, a hydraulic actuator for controlling the delivery of ?uid from the rapid
shifting the carriage toward the work piece, a traverse pump to said actuators, and ?uid con
second hydraulic actuator for moving said ducting means extending between the ?rst and
carriage longitudinally of the work piece, a third third actuators, whereby the movement of one
25 hydraulic actuator for shifting the rear carriage, of said carriages may be accurately timed with 25
a pumping mechanism for supplying ?uid under respect to the movement of the other carriage
pressure, a valve mechanism for controlling the » when the valve mechanism is positioned for
delivery of ?uid from said pump to said actuators, rendering the rapid traverse pump functionally
and ?uid conducting means extending between operative.
30 two of said hydraulic actuators, whereby the
56. In material working apparatus, a rotatable 30
movement of one carriage may be accurately work support, a front carriage shiftable toward
timed with'respect to the movement of the other and away from and longitudinally of the work
piece, a rear carriage shiftable toward and away
carriage.
from the work piece, a hydraulic actuator for
' 52. In metal working apparatus, a rotatable
work support, a front carriage shiftable toward shifting the carriage toward the work piece, a 65
and away from and longitudinally of the work second hydraulic actuator for moving said car
piece, a rear carriage shiftable toward and away riagelongitudinally of the work piece, a third
from the work piece, a hydraulic actuator for hydraulic actuator for shifting the rear carriage,
shifting the carriage toward the work piece, a a feed pump for the second hydraulic actuator, a
40 second hydraulic actuator for moving said second feed pump for the third hydraulic actu 40
carriage longitudinally of the work piece, a third ator, a rapid traverse pumping mechanism, a
hydraulic actuator for shifting the rear carriage, valve mechanism for controlling the connection
a pumping mechanism for supplying ?uid under of the rapid traverse pumping mechanism with
pressure, a valve mechanism for controlling the said actuators, and ?uid conducting means ex
45 delivery of ?uid from said pump to said actuators, tending between two of said’ hydraulic actuators, 45
and ?uid conducting means extending between whereby the movement of one carriage may be
the ?rst‘and third hydraulic actuators, whereby accurately timed with respect to the movement
the movement of the rear carriage toward the of the other carriage.
57. In material working apparatus of the class
work piece may be accurately timed with respect '
to the movement of the front carriage toward the described, a rotary spindle, a carriage shiftable 50
transversely of the spindle, a second carriage
work piece.
53. In metal working apparatus a rotatable shiftable transversely of’ said spindle, a hydraulic
work support, a front carriage shiftable toward actuator connected with each carriage, a closed
and away from the work piece, a rear carriage hydraulic circuit which includes one of’ said ac
tuators and also includes a feed pump, a rapid 55
55 shiftable toward and away from the work piece,
a hydraulic actuator connected with the front traverse pump, means for controlling the opera
carriage, a second hydraulic’ actuator connected , tive functioning of said latter pump with respect
with the rear carriage, a rapid traverse pump, a to at least one of said actuators, and ?uid con
feed pump, a valve for controlling the connection necting means extending between said actuators,
to of the rapid traverse ‘pump with said actuators, whereby the movement of one carriage may be 60
and connecting means extending between said accurately timed with respect to the movement
actuators, whereby the actuator of one carriage of the other carriage during the operative func
serves as an impeller for the actuator of the other tioning of said rapid traverse pump.
58. In material working apparatus of the class
carriage when said valve is positioned to render
the rapid traverse pump functionally operative. described, a rotary spindle, a carriage shiftable‘
54. In metal working apparatus; a rotatable transversely of the spindle, a second carriage
work support, a front carriage shiftable toward shiftable transversely of said spindle, a hydraulic
and away from the work piece, a rear carriage actuator connected with each carriage, a closed
' shiftable toward and away from the work piece, hydraulic circuit which includes one of said actu
a hydraulic actuator connected with the front ators and also includes a feed pump operable in 70
receiving and thereby the delivery of ?uid from
’ » ‘with'the rear carriage,'a rapid traverse pump, a
synchronism with said spindle, a rapid traverse
pump, means for controlling the operative func
feed pump, a valve for controlling the connec
tion of the rapid traverse pump with said actua
tors, connecting means extending between said
tioning of said latter pump with respect to at
least one of said actuators, and ?uid connecting
means extending between said actuators, where-'
carriage, ‘a second hydraulic ‘actuator connected
15
14»
2,078,696
by the movement of one carriage may be accu
rately timed with respect to the movement of the.
other carriage during the operative functioning
of said rapid traverse pump.
59; In material working apparatus of the class
described, a plurality- of shiftable machine ele
ments, a hydraulic actuator connected with each
controlling the actuation of said unitary valve
mechanism.
65. In combination with aplurality of shift
able tool carriages, a ?uid operated actuator
connected with each tool carriage, a single source
of ?uid supply connectable with one of said ace
'tuators, a second of said actuators being con
of said elements, a pump, a valve mechanism for - nected with and operated by said last mentioned
controlling the operative connection of the pump actuator, and means operated by one of said
'10 with said actuators, said valve mechanism in
cluding a plurality of shiftable valve members,
and means for unbalancing the ?uid pressure
within said valve mechanism, whereby to e?ect
the sudden shifting of said valve members.
60. In material working apparatus of the class
described, a plurality of shiftable machine ele
ments, a hydraulic actuator connected with each
of said elements, a pump, a valve mechanism for
controlling the operative connection of the pump
20 with said actuators, said valve mechanism in
cluding a plurality of shiftable valve members,
and means for reducing ?uid pressure in a por
tion of said valve mechanism, whereby to enable
the normal ?uid pressure in another portion
25 thereof to effect the sudden shifting of said mem
bers.
'
' 61. In material working apparatus of the class
described, a shiftable machine element, a hy
draulic actuator connected with each element, a
30 pump, a valve mechanism for controlling the
operative connection of the pump with said ac
tuator, said valve mechanism including a cylin
drical chamber and a valve member longitudinal
ly shiftable within said chamber, and means
35 shiftable longitudinally of said chamber to effect
the unbalancing of ?uid pressure therein and
thereby cause a sudden shifting of said valve
member.
62. In combination with a plurality of shift
able tool carrying devices, a ?uid operated actua
tor associated with each of said tool carrying de—
vices, a pump for supplying ?uid under pressure,
a valve for controlling the delivery of said ?uid
under pressure to one of said actuators, ?uid ‘con
45 ducting means‘ for effecting the starting and
speed of a second of said actuators in response
actuators for controlling the delivery of ?uid 10
from said single source of supply to the other
actuator.
->
66. In material working apparatus of the class
described, a plurality of ?uid operated actuators,
machine elements connected with said actuators -
and driven thereby, a single source of low pres
sure large displacement ?uid supply, a valve
mechanism for controlling the delivery of ?uid
from said source of supply to one of said actu
ators, means connecting said actuator with a 20
second actuator, whereby fluid from the ?rst
actuator may be forced toward the second actu
ator for shifting same, a high pressure ?uid dis
placing means connected with said second actu
ator, driving means for said high pressure ?uid ‘
displacing means, and means for controlling the
operative functioning of said ?uid displacing
means, said controlling .means operating to ren
der the high pressure ?uid displacing means
functionally inoperative during a portion at least
of the operating cycle of said actuators.
67. In material working apparatus of the class
described, a machine frame, rotary supporting
means, an oscillatoryand reciprocable tool sup- '
port, a second reciprocable tool support, a ?uid
operated actuator connected with each tool sup
port, means for supplying ?uid under pressure
to one of said actuators, means connecting said
last mentioned actuator with the second actu—
ator,'whereby the movement of the second actu- ..
ator is controlled by said ?rst actuator, and
means operable by the tool support associated
with one of said actuators for controlling the
connection between the source of ?uid supply
and said ?rst actuator.
a
68. In a hydraulic actuator system, a plural
to the actuation of said ?rst mentioned actuator, ity of ?uid operated actuators, each of, said ac
and means shiftable in response to the actuation tuators including a cylinder and a piston recip
of one of said actuators for controlling the ac - rocablev therein, means for supplying ?uid under
50 tuation of said valve.
'
,
pressure to one of said actuators for effecting 50
63. In a hydraulic actuator system, a plurality the shifting thereof, a duct connecting said last
of ?uid operated actuators, a machine element mentioned actuator with a second actuator,
connected to each of said actuators and shifted whereby ?uid may be forced from said ?rst ac
thereby, pump means for supplying ?uid under tuator to e?ect the shifting of said second actu
55 pressure, a valve for directing ?uid under pres
ator, and valve ‘means associated with said duct
sure to one of said actuators, a duct connecting for controlling the direction of ?uid ?ow between
said last mentioned actuator with a second ac~
tuator, whereby the speed of said second actuator
is
controlled by the ?uid displaced from said ?rst
60
’ actuator, rotary carryingmeans, driving means
therefor, and means operable in response to one
of said actuators for controlling the connection
between the carrying means and said driving
65
means.
-
' 64. In a hydraulic actuator system, a plurality
of ?uid operated actuators, a machine element
driven by each actuator, a single pumping mech
anism for supplying ?uid under pressure, a uni
70 tary valve mechanism for directing ?uid under
pressure to one‘ of said actuators, means con
necting said. actuator'with a second actuator,
whereby to control the starting and speed of
said second actuator, and means operated in
timed relation with one of said actuators for
said actuators.
69. In a hydraulic system 'for controlling a plu
rality of ?uid operated actuators, a ?uid pump
mechanism for propelling one of said actuators 60
at a feeding rate, a second ?uid pumping mech
anism for propelling another of said actuators
at a feeding rate, a third fluid pumping mecha
nism for propelling said actuators at rapid trav
erse speed, one of said actuators being con
trolled directly in response to another of said
actuators, a valve mechanism for selectively con
trolling the delivery o-f ?uid from said pumping
mechanism to said actuators, shiftable mecha
nism driven by one of said actuators, means on
said shiftable mechanism for timingly controlling
the actuation of saidvalve mechanism, a second
valve mechanism for independently controlling
the ?uid in connection with one of said actu
ators, and means on said shiftable mechanism
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