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Патент USA US3095012

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June 25, 1963
3,095,002
D. v. HEALY
DRY TYPE HYDRAULIC SERVO VALVE
2 Sheets-Sheet 1
Filed June 20, 1961
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June 25, 1963
3,095,002
D. v. HEALY
DRY TYPE HYDRAULIC SERVO VALVE
2 Sheets-Sheet 2
Filed June 20, 1961
85
90
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FIG.6
ic
&li-95,002
Patenta& June 25, 1963
2
&095302
DRY TYFE HYDRAULIC SERVO VALVE
_
Donald V. Healy, Newhall, Calif., assignor to The Bcn?l?x
Corporation, North Hollywood, Calif., a corporat?on
of Delaware
Filed June 20, 1961, Ser. No. 11%,373
5 Claims. (Cl. 137-235)
free end of the torque tube carries the armature and is
mechanically joined to the end of a shaft closing the end
of the tube. The opposite end of the shaft extends
through the torque tube into the housing and carries a
baf?e plate. T'?he torque tube seal furr?ishes an emcient
?uid seal and motion-transmitting member.
However, the art has serious need for a dry coil type
servo valve employing self-clearing operation of the type
accomplished by the invention of my Patent No. 2,823,
This invention relates to hydraulic servo valves and,
689.
more particularly, to “dry" type valves employing a hy
lt is a general object of this invention to provide a self
draulic housing containing all of the ?uid-conducting pas
clearing dry coil type servo valve.
sages and chambers and an external motive assembly in
Another object is to provide a self-cleariug servo valve
cluding a coil and armature sealed from the hydraulíc
in which the self-clearing operation takes place with mini
housing but operatívely connected to control the ?ow of
mum movement of the armature or disturbance of its nor
?uid through the valve in response to electrical signals ap 15 mal dynamic equilibrium condition.
Another object is to provide a servo valve having im
plied to the coil.
My patent 2,823,689, issued February 18, 1958, teaches
how the accurate control of ?uid ?ow through a servo
proved stability when subject to acceleration force.
One further object is to provide a simple, effective,
feedback
connection from the valve spool to the baf?e
ically .movable armature resiliently supported, including 20 plate.
a pair of end portions positioned :as ?ow-intercepting
Still another object is to provide a servo valve includ
baffles in front of a pair of parallel nozzles. With the two
ing internal feedback from the valve spool and, addi
nozzles communicating through restrictors to a common
tionally, provision for external feedback or external over
supply of hydraulic ?uid, the pressure at the nozzles is a
riding controls.
25
function of the relative positioning of the armature with
These objects are accomplished in accordance with this
respect to the two nozzles. Passages communicate be
invention, one embodiment of which comprises:
tween the nozzle regions and the opposite ends of a valve
A ?uid housing including a pair of Parallel disposed
cylinder containing a spool or piston which controls the
nozzles in the arrangement disclosed in my above-identi
main output ?ow of the valve. Where the armature is
?ed patent with, however, a dual-arm ba?ie plate posi
normally positioned in the order of 0.001" from the noz 30 tioned opposite the outlets of the two nozzles. The baf?e
zle tips, slight movement of the armature under the con
plate is mounted on a central shaft which extends out of
trol of an electrical signal applied to the armature's coil
the housing through a torque tube. The outermost end
valve may be accomplished employing an electro-magnet
creates a pressure differential between the two nozzles re
of the torque tube and shaft are sealed together and se
sulting in an ampli?ed force differential applied to the
cured to the armature of the driving motor. Operatively
ends of the valve spool or piston. By careful design of 35 »associated with the armature .are a pair of coils and a
the ?assembly, a servo valve is produced in which the main
magnetic structure. The nozzles within the ?uid hous
?ow through the valve, determined by the position of the
ing are connected to a common ?uid pressure supply and
spool, is -a linear function of the current ?ow through the
to a branch circuit to the ends of the Operating sleeve con
energizing coils associating with the armature.
40 tained in the spool or piston.
In my patent, above identi?ed, one particular problem
The shaft carrying the baf?e bar extends below the
common to servo valves is recognized, and the resilient
bathe plate in reduced section, the end of which is coupled
mounting of the armature offers a solution. The prob
to the spool of the Operating cylinder to provide mechan
lem is that regardless of the ?ltering of the hydraulic ?uid
ical feedback between the spool and the ba?ie plate and
used, often particles of dust or dirt `are carried in the ?uid 45 thereby provide a restoring force opposing that of the
and lodge between the nozzle tip and the armature. The
input signal.
novel suspension system for the „armature allows the
In another embodiment, the support structure for the
armature, in the presence of dirt particles, to move out
Ward from the nozzle, allowing the particles to be dis
armature and baf?e plate extend out of the motor space
to allow for external feedback or overriding control of
lodged with only momentary disturbing of the existing 50 the electrical input.
pressure di?erential between the two nozzles and thereby
One feature of this invention resides in a dry coil servo
not signi?cantly affecting the position of the spool. This
valve in which a composite structure made up of a torque
self-clearing feature provides reliable operation.
tube and a rigid shaft mount a dual-arm baf?e plate for
Recently the desirability of eliminating all contact be
rotational and translational movement.
_
tween the motor portions of servo valves and the hydraulic 55 Another feature resides in mounting the armature and
?uid has been recognized. This has given impetus to the
ba?le plate o?set from their axis of rotation at a right
design of `so-called “dry coil” servo valves in which all
angle with respect to the direction of travel of the valve
fluid ?ow, in particular, the discharge from the nozzles,
spool so that acceleration forces tending to ?move the
takes place in a housing which is sealed from the armature
spool also aífect the baf?e plate and armature in a man
pole pieces and coil. With this arrangement the arma
ner which compensates the acceleration forces on the
60
ture of course cannot be located in proximity to the dis
spool.
charge nozzles so that an auxiliary member (having the
Still another feature involves a second torsion spring
same general shape as the armature) and variously called
for the baf?e plate for introducing feedback from the valve
a ?apper or baf?e plate, ?hereinafter referred to as a ba?ie
plate, is positioned adj-acent the nozzles and is coupled to
spool.
One further feature resides in the extension of the baf?e
the armature through a sealed connection in the wall of 65 support through the motor housing to provide a point for
the housing.
~
One particularly desirable scaling arrangement for dry
type servo valves is disclosed in Patent No. 2,905,871 to
external torque input to the system.
These and other features of this invention may be
clearly understood from the following detailed descrip
L. Martin, issued September 22, 1959, and assigned to the
tion with reference to the drawing in which:
assignee of this invention. That sealing arrangement in~ 70 FIG. 1 is a Vertical sectional View through the motor of
volves the use of a torque tube extending out of the sealed
housing and secured thereto at one end. The outer or
a servo valve incorporating this invention;
i
`
3
FIG. 2 is a vertical section through the entire servo
the shaft 34, shaft 51, feedback arm 53 and, most im
portant, ba?le plate 40, are all located, is exposed 'to :the
:drain pressure of the system, and it is in this chamber
' FIG. 3 is a horizontal section through the nozzle 'block
where the nozzles 43 and 4-4 discharge ?uid. The motor
portion of the valve or" FlG. l;
elements, of course, are all outside of the housing 10 and
FIG. 4 is an isometric projection of the valve of FIG. l;
are sealed therefrorn by the torque tube 31.
FIG. 5 is a longitudinal section -to the valve sleeve and
The eleotrical input to the motor is through a pair
spool along lines 5-5 of FIG. 1; and
of leads 65 which enter a side opening in the housing 10
FIG. 6 is a fragmentary sectional View of another em
and pass through a ?ange portion 70 of the housing 10,
bodiment of the invention.
Now referring to FIG. 1, the servo valve incorporating 10 through the nozzle block 11 and into the motor cavity
without entering the hydraulic housing proper.
.this invention consists basically of a hydraulic housing 10
valve of FIG. 1 taken in the plane at right angles with
respect to the plane of the section of FIG. I;
closed by a nozzle `block 11 to which is secured the motor
operation, Generally
assembly 12, the last within a cap 13. Motor assembly
, The operation of the servo valve is best understood
12 comprises a pair of bar magnets 14 and 15 mounted
:to introduce ?ux into 'a pair of ferromagnetic frame mern 15 from the simpli?ed isometric showing of FIG. 4. The
purpose of the valve is to apply a controlled ?ow in and
:bers 16, one of which is shown in the drawing. The ?rame
out of 'two cylinder ports 70 and 71, which ?ow is a
members 16 include arms 20 ter-minatin-g in %faces '21 and
linear function of the magnitude of the current passing
22 opposite the ends of an armature 23 mounted for ro
through a pair ot terminals 74. The :output ports 70 and
;tation on 'a supporting arm 24, as best seen in FIG. 2.
The armature 23 passes through central openings 27 in a 20 71 are normally connected to opposite ends of a double
acting piston 72 within an actuator cylinder 73. Move
pair of coils 25 and 26. Coils '25 and 26 are held in
ment of the piston '73 is accomplished upon longitudínal
place within the encl-osure made by the frame member 16
movement of the valve spool 56 from the intermediate
by a pair of spring clips 30, one of which appears in
ne-utral position toward one end whereby one of the cylin
FIG. 1.
der
ports 70 or ”71 eis connected to the pressure source,
The armature 23 is lightly held midway -between the
and the other cylinder port is connected to the drain
:opposing faces 21 and 22 of the magnetic frame members
port 62. controlled movement of the valve spool 56 is
16, for movement from the mid position ,under the control
accomplished by applying hydraulic pressure to a pair of
of changes in ?ux in the magnetic system resulting from
passage of current through .the coils 25 and 26, as well as
.pressure ports 90 and 91 ?from a ?uid source 80 by means
from the reaction -or feedback forces from the hydraulic 30 of a pump 81 and a main pressure line'82. The ?uid is
introduced through line 82 into an inlet chamber 83 con
spool as hereinafter described.
taining a ?lter 84. The main hydraulic ?uid path ?by
The interaction between the .motor assembly 12 and
passes the ?lter 84 ?owing through .the enlarged central
the hydraulic assembly within housing 10 -is more clearly
section of chamber 83 and a pair 'of passages '85 and 86
seen in FIGS. 2 and 3. In FIG. 2 the arm 24 supporting 35 to the annular pressure ports 90 and 91 of the valve sleeve
armature 23 in .the opening 27 of coil 25 is carried itself
or cylinder 92. The pressure ports 90 and 91 are closed
by an upstandíng tubular support, hereinafter designated
:by respective lands 93 and 94 When the spool 56 is in its
the torque tube 31, including enlarged collar portion 32
position. The ends of the ?lter chamber 83 are sealed
sealed in an opening 33 in the nozzle block 11 of the hy
from the inlet port 82 by the ?lter 84 'so .that hydraulic
draulic assembly. The upper or free end of torque tube 40 ?uid reaching the end portions passes through the ?lter
*31 is closed by a central shaft member 34 sealed therein
8-4, and contaminants, in particular, particles of su?icient
Vas 'by brazing. The seal between the shaft 34 and tube
size -to plug restrictors 95 and '96 or interfere with :the
31 must be adequate to resist at least the drain or return
operation of the di?erential nozzle mechanism herein
hydraulic pressure and prevent the ingress of hydraulic
after described, are retained. The ends of ?lter chamber
?uid from the housing 10 into the motor space rof the
83 communicate through the ?ow restrictors 95 and 96
valve. The tube 31 is preferably .of a spring material,
and passages 100 and 101 with .the pair of nozzles 43- and
such as beryllium Copper, having a thin wall in the order
44 respectively positioned .in substantially parallel rela
of 0.006" to allow the rotational movement of the arma
rtionship and each including an outlet ori?ce 45 or 46
ture 23 about the aXis of the tube 31 by twisting of the
directed toward opposite ends of the `baflle plate 40. The
tube 31. The `rotation of armature '23 is transmitted 50 passage 100 includes a branch passage 106 communicating
through shaft 34 into the housing 10. The shaft 34- car
with one end of the valve sleeve 92. A branch passage
ries a ba?le plate 40, best seen in FIG. 3, including a pair
110 from the passage 1011 communicates with the opposite
of end bathe portions 41 and 42 directly opposite the ori
end of sleeve 92.
?ces in nozzles 43 and 44 respectively. A nominal spac
ing between the ba?le portion of plate 40 and the respec 55
No S?'g??al Operating Condition
tive nozzles is in the order of 0.001", and movement from
In
normal
operation with the valve connected to a
the nominal position varies under maximum signal condi
,source of hydraulic pressure and no signal -applied to the
?tions from 0 .to 0.001" in either direction.
terminals 74, hydraulic ?uid ?ows trom the pump 81
Referring again to FIG. 2, the lower end of shaft 34 in
through
passage 82 to the ?lter chamber 83 from which
cludes a reduced diameter portion 50 constituting a tor 00
it passes directly to the pressure ports 90 and 91 of the
sion spring extending into and secured at its lower end
valve sleeve. The lands 93 and 94` cover the pressure
to a rigi?d hollow shaft 51 tor transmitting torque from a
ports
90 and 91 so that the outlet ports 70 and 71 both
feedback arm 53 to the ba?le plate 40. The shaft 51 is
are exposed to equal pressure, to wit, -a Value approxi
journaled in a hearing 52 secured to the nozzle block 11
mately half-way between the system inlet and drain pres
and has at its upper or tree end an arm 53 secured thereto 65
sure
due to tleaka?ge past the lands. Hydraulic ?uid pass
and extendin?g to one side and terminating in a `rdepending
ing :through the ?lter 84 in the ?lter chamber 83 ?ows
?nger 54 which rests in annular slot 55 in the spool or
through passages 100 and 101 to respective orí?c?es 45 and
pisten 56 of the valve. The .arm 53, hollow shaft 5-1 and
46. In the no signal condition, the ba?le plate 40 is pre
torsion spring 50 provide a mechanical feedback between
cisely located lat equal distances from the ori?ces 45 and
the spool 56 and the baf?e plate 40.
70 46. Since both ori?ces are .fed by a common supply pres
The hydraulic Components of the valve in addition to
sure, and the pressure drops in the restrictors 95 and 96
.the spool 56 include: a ?lter 60 at the main inlet port 61,
are
equal, the pressure ?applied to› branch lines 106 and
a main return or drain port 62, and several communicat
110 is the same, and opposite ends of the valve spool 56
ing passages in the housing 10 and illustrated in schematic
V are exposed to the same forces. The spool 56 therefore
form in FIG. 4. The main internal cavity 63 in which 75
:remains in its centered position. Fluid emerging from
3,095,002
the ori?ces 45 and 46 strik-ing the bathe plate 40 falls into
the chamber 63, shown in FIG. 2, down to the drain port
62 .and returns to the ?uid supply 80.
Signal Condition Operat?'on
When a current ?ows through terminals 74 and the
coils 25 and 26, the magnetíc equirlibrium condition be
6
56 as well as the valve body rand may tend to move the
spool 56 with respect to its cylinder or sleeve. Any force
Components acting transverse to the axis ot the sleeve 92
are ine?ective to change the position of the spool 56.
However, forces acting along the -line of the sleeve or
valve cylinder 92 axis will tend to move the spool, result
ing in unwanted and uncontrolled movement of the oper
tween the faces 21 and 22 of the pole pieces 16 is changed
ating piston "12.
so that one end of the armature 23 is drawn toward one
tion of several “G”s” in the direction of the upper left
For example, if the valve body is subject to accelera
pole piece, and the opposite end of the armature 23 is 10 hand corner of FIG. 4, the spool 5.6, owin-g to its rela
drawn toward the ?opposite pole piece. This movement
tively large mass, will tend to move toward the lower
is about the axis of torque tube 31. Rotation of the arma
right-hand corner of the drawing with respect to the valve
ture 23 is accomplished by torsion-induced twisting of
body. Such movement can be su?icient to vary the ?ow
the tube 31 which is readily accomplished, since thin wall
of ?uid through ports 70 and 71 and be interpreted by
:spring material tubing is used. Twisting of the torque 15 the operating piston as a command signal. However, it
tube 31 permits rotation of the shaft 34 within tube 31
should be noted that both the armature 23 and ,the ba?le
and rotational displacement of the bañ'le plate 40. The
bar 40 are mounted eccentrically on the shaft 34. Both
movement of bafñe pl-ate 40 in rotation duplicates that of
have centers of gravity, marked C. G. in FIG. 4, dis
the armature 23. For example, in the drawing (FIG. 4)
placed from the axis of rotation. Displacement is to
20
with command current of one polarity applied to the coil
ward the spool 56. whenever the valve is subject to ac
through termina'ls 74 such that the armature rotates in
celeration causing the spool to move, -as indicated before,
a clockwise direction as viewed from the top, the bafñe
toward the lower right-hand corner of the drawing (FIG.
plate 40 also rotates in a clockwise direction, moving the
4), the same force vacting upon the :bar 40` and particularly
?battle 42 in close proximity to ori?ce 46 while the baf?e 41
the
armature 23 tends to cause these members to` rotate
moves away from ori?ce 45. The pressure in the line 101 25 bodily in the counterclockwise direction, causing an in
increases because of the bathe restriction at .the ori?ce 46,
.crease in pressure at the nozzle 43 :similar to that encoun
while the .pressure in line 100 falls off because of the
tered by a command sign-al which produces a pressure un
opening up of ori?ce 45. The pressure changes in the
-balance between the lines 106 and 110 with a force dif
lines 100 and 101 are communicated through lines 106
ferentia-l actin-g upon the spool 56 in the opposite direc
and 110 to the ends of the cylinder 92, causing move 30 tion from the acceleration force, to wit, toward the upper
ment of the spool 5.6 toward the lower right in FIG. 4.
left in FIG. 4 in the example given. As a net result, the
This condition is` illustrrated as well in FIG. 5.
spool 56 does not move. Acceleration in the opposite
Movement of the spool 56 i?ntroduces torque through
direction results in similar compensating movement by
the hollow shaft 51 which opposes the armature torque
the armature 23 and p'late 40.
and tends to restore the 'bathe plate 40 to its previous posi
Therefore, valves incorpworating the eccentric armature
tion. An equil-ibrium condition in the moving elements
-and bañle plate automatically eliminate movement of the
of the valve is thereby established. As the spool 56 moves
spool 56 under the in?uence of accele?r?ation forces.
to the right, the pressure port 90 is uncovered as land 93
Multiple To?'que lnpuís
moves off the inner edge of port 90. The pressure port
90 then communicates with the cylinder port 71 while the 40
The servo valve of FIGS. l through 5 is designed for
cylinder port '70 is connected to the drain port 62. The
a single electrical input through the terminal 74 and has
pressure differential on the opposite ends of the piston 72
internal feedback from the valve spool. In certain appli
results in its movement to the left. The velocity of the
cations, it is desirable to have provision for external feed
-piston 72 depends upon the rate of ?ow, which is deter
back, for example, from the operated piston 72 itself or
mined by the extent of movement of the spool 56 from 45 from related ?apparatus. Additionally, it is sometimes
its neutral position. Spool 56 moves responsive to pres
desirable to :have provision for -an overriding manual con
sure differentials on its ends produced by displacement
trol for the valve in case of malfunction of the valve or
of the 'bafñe plate 40 from center position. The position
other parts of the system. In the past, complicated
of ba?le plate 40 in turn is determined by the summation
mechanisrns have been required to provide either of these
50
of armature and feedback torques. Armature torque is
additional inputs to servo valves. However, employing
a function of command signals ?applied to terminals 74.
the embodiment of FIG. 6, which is a modi?cation of the
Automatic Pressure-Comwpensatíon
same basic structure of FIGS. 1 through 5, the sumrn-a
tion of one or more inputs from manual, mech-anical,
Servo valves incorporating my invention automatically
hydraulic or electrical sources is possible. This is
compensate for changes in pressure similar to my valve 55 achieved by the presence of an upper extension of the
of Patent No. 2,823,689. The novel Ibaf?e plate mount
shaft 34 passing out through a hearing 130 and Secured
ing arrangement is symmetrica'l with respect to the axis
`to an input torque arm 131. The upper extension of shaft
of movement so that an increase in supply pressure pro
34 includes a reduced section 134 constituting -a torsion
duces an increase in pressure at both nozzles, resulting in
spring. The torque arm 131 may be quite short, ?because
equal forces applied to` both ends of ba?ie plate 40, and 60 only -a small torque input to the upper end of sh-aft 34 is
no rotational movement of battle plate 40 results. Lower
necessary in order to produce signi?cant movement of
shaft 50 is actually Suspended in the intermediate region
the armature 23 and the hafñe ?plate 40, unshown inthe
of a ?exural support, so that upon an increase of inlet
drawing.
'Dhe arm 131 may be connected `as ?a manual
pressure the upper ,and lower supports are bent outward
override control or as an `a-dditional torque input to the
while ?no rotation is imparted to either shaft because the 65 valve.
turning movement applied to both ends of the ba?le plate
In the embodiment of FIG. 6, a lower torsion spring
40 is equal. With the reduction in inlet pressure, the bat
portion 151 of shaft 34 extends through a hearing 152
?e plate 40 moves =bodily toward both nozzles 45 and 46
out of the housing 10. A torque -arm 153 may be suit
-ably attached to the extension 150 to provide `an addition
without rotational motion.
70 al torque input to the system. The lower input through
Acceleratíon Force Stab?'l?'íy
I?nproved stability under acceleration conditions is
achieved employing this invention. It is apparent that
the spring section 151 is particularly adapted tor the intro
duction of feedback from the Operating cylinder or other
parts of the hy?draulic system, since it extends out of the
when the valve structure `as shown in zFIG. 4 is subjected
hydraulic side of the valve. Where torque over 153 is
to acceleration forces, those forces will act upon the spool 75
7
3
connected to the controlled mechanisms to provide feed
back, the feedback path 'from spool 56 may be unneces
sary or undesirable and may be eliminated.
It should .be noted that any number of additive input
forces in the system are possible by extending either the
an elongated ?ba?le including portions' for restricting
?ow from said nozzles to vary the pressure of hy
draulíc ?uid at said nozzles;
a cylinder;
a spool positioned within said cylinder;
upper or lower end of the shaft 34 and attaohing addi
tional torque arms. This is all possible because the funda
means communicating the ?uid pressure at said nozzlcs
to opposite ends of said spool to vary the position of
mental motion of the baf?es within the valve is obtained
by torque input to its support member, the shaft 34.
said spool dependent upon the pressure differential
of said nozzles;
Although for the purpose of explaining the invention a 10
particular embodiment thereof has been shown and de
a coil external to s-aid housing including terminals for
scribed, obvious modi?cations will occur to a person
skilled in the art, and I do not desire to be limited to the
exact det-ails shown and described.
'an armature for said coil;
?applying an electrical signal thereto to energize said
coil;
I I claim:
15
1. A servo valve comprising:
a hydraulic housing;
a ?ow-control system within said housin-g including -a
pair of substantially parallel ?directed nozzles and an
elongated baf?e having spaced portions positioned to
a torque tube sealing said housing from said coil and
:mounting said armature for rotational motion upon
the enengizing of said coil;
?a shaft within said torque tube extending into said
housing and mounting said ba?ie in position opposite
'said nozzles and symmetrically therewith Whereby
?'otation of said armature and shaft rotates said ba?ie
to restrict one and relieve the other of said nozzles;
vary the ?ow of ?uid from respective nozzles;
a motor compartrn'ent;
said ba?ile being resiliently mounted by said torque tube
motor means within said compartment;
to move bodily toward or away from said nozzlcs re
means sealing said hydraulic housing from said motor
sponsive to ?uid pressure changes thereat;
25
rand torsion spring means coupled `between said shaft
said sealing means comprising a nonrigid tube with one
and said spool constituting a mechanical feedback
end sealed to said hydraulic housing 'and a shaft seal
connection between said spool and said ba?le.
ing the free end of said tube and extending through
4. An electrohydraulic servo valve employing mecbani
said tube;
cal feedback comprising:
said shaft coupled to a point midway between the
compartment;
spaced portions to transmit torque from said motor
means to said ba?'ie to vary the relative spacing of
said -baf?e spaced portions with respect to said nozzles
30
tively parallel relation-ship;
va common hydraulic ?uid pressure source for said
simultaneously in opposite sense;
said tube and shaft supporting said ba?le for simultane
nozzles;
an elongated baf?e including portions for restricting the
ous translation movement in the same sense toward
?ow from said nozzles and to vary the pressure of
`and away from said nozzles in response to ?uid pres
sure ohanges thereat.
2. A servo valve comprising:
hydraulic ?uid at said nozzles;
a valve cylinder; .
a spool positioned within said cylinder;
a pair of gener-ally parallel-positioned nozzles;
means ?commun?icatinwg the ?uid pressure at said nozzlcs
to the opposite ends of said spool to vary the position
a source of hydraulic ?uid pressure for said nozzles;
baf?es positioned for restricting the ?ow of hydraulic
?uid from said nozzles;
a motor including -an armature 'for controlling the ?ow
of ?uid through ,said valve;
and means positioning said ba?ie for rotational motion
toward one nozzle and away from the other nozzle
upon the energizing of said motor, and for simultane
45
changes of said hydraulic ?uid pressure source;
said positioning means comprising a torque tube mount
ing said armature and ba?le' for rotatíonal motion
of control torque to said valve.
torque tube;
References Cited in the ?le of this patent
and a rigid member Secured to the armature end of said
UNITED STATES PATENTS
torque tube and mounting said ba?ie for translation
al motion by ?exural „distortion of said torque tube.
3. An electrohydraulic servo valve comprising:
`
tively pa?r?allel relationship;
a common -hydraulic ?uid pressure source for said
nozzles;
of said baí?e and said spool.
5. The combínation in .accordance with claim 4 where
_in said support for said bañle extends out of the valve,
thereby constituting an input connection -for application
under the in?uence of said coil by twisting of said
v
ber;
spool and said baf?e for introducing torque into said
bame-supporting means upon relative displace?nent
or away from said nozzles responsive to pressure 60
a housing;
of 'said spool, dependent upon the pressure diñerential
-at said nozzles;
means supporting said baf?e including a torsion mem
and a second torsion member coupled between said
ous translational movement in a same sense toward
a pair of nozzles within said housing positioned in rela
a hydraulic housing;
a pair of nozzles within said housing positioned in rela
GO
2,823,689
2,835,265
2,9i33,106
2,942,581
3,054,416
Healy ______________ __ Feb.
Brandstadter _________ __ May
Gerwig et al __________ __ Apr.
Gaffney _____________ __ June
Lucien ______________ __ Sept.
18,
20,
19,
28,
18,
1958
1958
1960
1960
1962
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