Combined servo control and jack unit

There is disclosed a combined servo control and jack unit which comprises a casing, an actuated piston slidably disposed in a piston chamber and having a piston rod extending outwardly of the casing. A servo valve chamber, axially parallel to the piston chamber, has slidably mounted therein a spool and also a sleeve member which is mechanically connected to the piston rod. Shifting the spool in either axial direction directs hydraulic fluid to one or the other side of the piston, thus moving the latter until spool stopping, at which time the sleeve automatically, almost instantly, blocks off the flow in the new position. A variable speed, gradual action of the piston is obtained without hydraulic shock or cavitation.

FIELD OF THE INVENTION 
The present invention relates to a combined servo control and jack unit for 
regulating the position of an adjustable member, such as the cam plate or 
swashplate of variable displacement pumps and hydraulic motors as well as 
the spool of slide valves and distributors. 
BACKGROUND OF THE INVENTION 
Known units of this type often lack in positioning precision and/or are of 
complex and expensive construction. 
OBJECTS OF THE INVENTION 
It is a prime object of the present invention to provide a servo control 
unit embodied by the combination of a servo valve and hydraulic jack 
adapted to very accurately control variable displacement piston pumps and 
the like. 
Other objects of the invention are to provide a unit of the character 
described, which is safe to use and which obviates the problems of 
hydrualic hammer and cavitation. 
It is another object of the present invention to provide a servo control 
unit of the above type, which is simple in design and non-costly to 
manufacture. 
SUMMARY OF THE INVENTION 
The above and other objects and advantages of the present invention are 
realized according to a preferred embodiment comprising a rigid, 
preferably box-shaped casing, adapted to be fixed to a stationary 
structure. The casing is formed with a longitudinal piston chamber 
extending preferably from end to end. One of the ends is closed and is 
preferably provided with a stroke-regulating means for the piston. The 
opposite end is closed by a suitable collar member formed with a central 
longitudinal bore through which extends the rod of the piston. The rod 
extends outwardly of the casing and has an outer end secured to, for 
example, a camplate or swashplate control arm. The piston is of the 
double-action type, being adapted for longitudinal displacement in either 
direction in the chamber. 
The casing is further formed with a servo valve chamber also extending 
longitudinally from end to end and which is spaced apart from and parallel 
to the piston chamber. 
A spool extends into the servo valve chamber from either end of the casing. 
Biasing means may be provided to maintain the spool in centered neutral 
position. The spool is slidable in either direction from its neutral 
position under the action of suitable control means. 
An elongated sleeve member also extends inwardly into the servo valve 
chamber, from one end of the casing. The outer end of the sleeve is formed 
into an axial shaft externally of the casing. The inner portion of the 
sleeve closely surrounds the inner portion of the spool. 
One of the longitudinal casing walls adjacent the valve chamber is provided 
with a fluid inlet port, which communicates with the servo valve chamber 
and which is preferably to be connected to a hydraulic source under 
pressure. The same wall is further provided with a fluid outlet port which 
also communicates with the servo valve chamber and which leads to a sump. 
The two ports are longitudinally spaced from each other. 
The inner portion of the sleeve and the contiguous inner portion of the 
spool which extends inside the sleeve are cooperatively constructed and 
arranged to selectively direct the incoming flow of fluid from the inlet 
port into one or the other of two spaced-apart entry orifices formed in 
the sleeve, when the spool is actuated. One of the orifices communicates 
with a first channel formed in the middle portion of the casing, which in 
turn communicates with one side of the piston chamber. The other entry 
orifice communicates with a second channel, also formed in the middle 
portion of the casing and which communicates with the other side of the 
piston chamber. The channels do not communicate with each other. 
Upon such actuation of the spool, one or the other of two spaced-apart exit 
orifices, also provided in the sleeve, selectively, almost simultaneously, 
direct the outflow of fluid into one of two paths to the outlet port, 
depending on the direction of actuation of the spool. The exit orifices 
have a cross-sectional size smaller than that of the entry orifices to 
cause a back pressure in the lower pressure side of the piston chamber. 
This reduces cavitation and hydraulic hammer. 
The shaft end of the sleeve and the outer end portion of the piston rod are 
joined by direction-reversing mechanical linkage means. Thus, actuating 
the spool in one direction causes the piston to move in the opposite axial 
direction and, via the linkage, causes the sleeve to move in the same 
direction and the same displacement as the spool. 
Preferably, relative displacement limit means are provided between the 
spool and the sleeve.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
The servo control unit 1 according to the invention is shown with all the 
movable elements in neutral centered position, in all FIG. 1. Unit 1 is 
housed in a box-shaped monoblock casing having a top wall 2, a bottom wall 
3, a pair of opposite end walls (not seen) and a pair of longitudinal side 
walls (also not seen). The end walls, the top wall 2 and the bottom wall 3 
have plugs 4 closing the outer ends of bores, these outer ends being for 
machining purpose only. 
The monoblock casing may be made of an extruded metallic alloy, such as the 
alloy known by the trademark name &gt;&gt;DURALUMIN&lt;&lt;, or again by a cast 
aluminum-bronze laminate. Any other suitable material could be used. For 
alkaline or acidic mediums, stainless steel is preferred. The casing may 
be made in any size according to particular applications. 
All the various elements which project exteriorly of the casing are 
preferably made of chromed carbon steel. 
Referring to the lower portion of FIG. 1, there is shown the piston chamber 
5, which extends longitudinally from end to end of the casing. One end of 
chamber 5 is sealingly closed. Preferably, this closure is formed by a 
piston stroke regulating means, consisting of a collar 6 threadedly 
engaged in the casing and sealed by an O-ring seal 7. Collar 6 carries a 
large set-screw 8 threadedly engaged therein. The inner unthreaded end 9 
of screw 8 forms a piston abutment, whose longitudinal position is 
adjustable by turning set screw 8, one way or the other. Another O-ring 
seal 10 is provided to prevent fluid from flowing into the bore of collar 
6. A closure cap 11 is integral with the outer end of collar 6 and 
compresses O-ring 7. A lock nut 12 effectively prevents movement of the 
set-screw once adjusted. 
A piston 13 is slidably mounted in chamber 5. Piston 13 has a pair of rings 
14. The opposite end of piston chamber 5 is closed by a second collar 15 
threadably engaged therein. Extending through collar 15 is a piston rod 16 
connected to the piston and having an outer end projecting exteriorly of 
the casing. The extreme outer end is flattened and formed with a hole 17. 
Collar 15 has an integral closure cap 18. O-ring seals 19 and 20 contact 
piston rod 16 and seal piston chamber 5. 
Preferably, a spacer ring 21 surrounds piston rod 16 and contacts the inner 
face of collar 15. 
Spacer ring 21 serves to shorten the stroke of the piston on that side of 
piston chamber 5. The thickness of ring 21 is selected for the specific 
application. 
The middle portion of the casing is formed with a first longitudinal 
channel 22 on the left side, as shown, and which communicates with piston 
chamber 5 by a passage 23. A second similar longitudinal channel 24 
communicates by a passage 25 with the opposite side of piston chamber 5. 
Referring now to the upper portion of the casing, as shown in the figures, 
a longitudinal servo valve chamber 26 extends from end to end of the 
casing in spaced-apart axially parallel relationship above piston chamber 
5. 
Servo valve chamber 26 has slidably mounted therein an elongated sleeve 27 
having a solid outer portion 27' which integrally merges with an outermost 
shaft portion 27", the latter being flattened at its extremity 28. The 
inner portion of sleeve member 27 is cylindrical, defining a bore 29 which 
opens into chamber 26. 
Sleeve 27 is held slidably sealed by a pair of annular seals 30, 31. 
The outer end of the piston rod 16 and the extremity 28 of sleeve 27 each 
have a transverse pivot stud 32,33, respectively. A pair of connecting 
arms 34 (only one is seen) are pivotally attached at their opposite ends 
to studs 32, 33 through slots 35, 36. The two arms themselves are pivoted 
about an intermediate transverse pivot 37, which is mounted on a 
horizontally-projecting member 38 fixed to the right side end wall of the 
casing by bolts 38'. 
At the opposite end of the casing, a spool 39 extends inwardly into slide 
valve chamber 26. The same end of the latter is sealingly closed by an 
elongated third collar 40, which has an inner portion threadedly engaged 
in casing 1 and sealed by an O-ring seal 41. This inner portion has a 
central longitudinal bore opening outwardly into an external larger 
diameter bore 42, which is open at its outer end. Spool 39 has a step 39' 
which defines a smaller diameter outer portion 39", the latter terminating 
inwardly at the inner end of large bore 42 when in centered position. A 
seal 42' is provided around spool 39. 
A connector 43, for the sheath of a flexible control cable, is screwed onto 
the outer end of collar 40. The flexible cable is screwed in an axial, 
threaded bore 39"' of spool portion 39". Connector 43 defines an annular 
shoulder 44. 
The biasing means disclosed above, to maintain the valve 39 in neutral 
position, consists of a pair of oppositely-disposed flanged sleeves 45 
slidable on spool outer portion 39" and between which is located a helical 
compression spring 46. All these elements are located in external bore 42, 
one of the flanged sleeves 45 abutting shoulder 44 and the other abutting 
a shoulder 42" at the inner end of bore 42. 
When spool 39 is pulled to the left by the control flexible cable, 
right-hand flanged sleeve 45 is pushed to the left by step 39' and this 
compresses spring 46 against left-hand flanged sleeve 45, which is 
retained by shoulder 44. When spool 39 is pushed to the right by the 
flexible cable, left-hand flanged sleeve 45 is pushed to the right by a 
split washer 45' retained on spool outer portion 39". This compresses the 
spring against right-hand flanged sleeve 45 which is retained by shoulder 
42". Control of spool 39 can, obviously, be obtained by other means than 
by a flexible cable. 
The inner portion of the spool 39 extends into the bore 29 of sleeve 27. A 
pair of longitudinally-spaced first and second circumferential bosses 47, 
48, respectively, are provided at the inner end and intermediate areas, 
respectively, of the spool 39. 
This inner portion of spool 39 is further made with an axial passage 49 
extending from the inner end of the spool 39 and terminating beyond outer 
boss 48. Slightly inwardly of the end of passage 49, spool 39 has a pair 
of slots 50 which communicate with passage 49 (see FIG. 2). Extending 
through slots 50 is a diametrically-projecting pin 51 which has its ends 
rigidly secured to the cylindrical portion of sleeve 27. Thus, sleeve 27 
and spool 39 are free to slide relative to each other for a distance not 
exceeding the length of slots 50. This arrangement constitutes the 
relative displacement limit means, also disclosed above. 
The diameter of both bosses 47, 48 is minutely less than the diameter of 
the inner surface of sleeve 27 at its cylindrical portion. This provides 
for sealingly slidable contact between the bosses of spool 39 and sleeve 
27 and further defines a sealed space 52 between the two bosses--when the 
spool and sleeve are in neutral position--except for the fluid inlet port 
53, which communicates constantly with this space 52. 
Top wall 2 is made with the fluid inlet port designated at 53, as well as a 
fluid outlet port 54. As shown, port 53 overlies space 52 and communicates 
with a wide slot-like aperture 55 formed in the adjacent portion of sleeve 
27, aperture 55 in turn communicating with a small bore 55', always in 
communication with space 52. 
Still referring to FIG. 1, the lower portion of sleeve 27, immediately 
under first boss 47, has a first pair of orifices consisting of an inlet 
orifice 56 and a closely, outwardly-spaced outlet orifice 57. Similarly, 
the portion of sleeve 27 immediately under second boss 48 has a second 
pair of orifices consisting of another inlet orifice 58 and another outlet 
orifice 59. Both inlet orifices 56, 58 are adjacent sealed space 52, while 
both outlet orifices 57, 59 are spaced away from sealed space 52. As 
shown, the outlet orifices 57 and 59 have smaller neck portions than the 
inlet orifices. Both the first and second pairs of orifices open out into 
wide slot-like openings 60,61, respectively, which communicate with 
channels 24, 22, respectively. 
Referring now to FIGS. 3 and 4, the operation of the servo control unit 1 
is depicted. In FIG. 3, the spool 39 is given thrust or movement from left 
to right, thereby moving first boss 47 sufficiently to unblock inlet 
orifice 56 and moving second boss 48 similarly to unblock outlet orifice 
59 of the second pair of orifices. Thus, fluid from sealed space 52 
between the bosses 47, 48 will flow through inlet orifice 56, into channel 
24 and so exert a leftwardly-acting force on piston 13 in chamber 5. 
Piston 13 will respond because fluid on the other side of chamber 5 will 
flow through channel 22, outlet orifice 59 and into slide valve chamber 
26. From the latter, the fluid exits through outlet port 54. As piston 13 
responds, connecting arms 34 will pivot about pivot 37, thereby causing 
sleeve 27 to slide porportionally in the same direction and for the same 
distance as the spool 39. As a result, sleeve 27 automatically reblocks 
both pairs of orifices and piston 13 is once again, and almost instantly, 
immobilized, so that piston rod 16 may control the position of the movable 
member of any device connected to its outer end. 
In FIG. 4, there is shown the reverse motion, wherein spool 39 is actuated 
by traction (in the drawing, movement from right to left). It will be 
clear that such movement will unblock the other inlet orifice 58 as well 
as the other outlet orifice 57. Piston 13 is then moved in the direction 
opposite to that of FIG. 3 and sleeve 27 again moves in the same direction 
as spool 39 to automatically reblock the orifices. The return path of the 
fluid is not the same as that shown in FIG. 3. However, instead of flowing 
directly into slide valve chamber 26 outwardly of the boss, the fluid is 
circulated through outlet orifice 57 into the end portion of bore 29. From 
there the fluid is directed to axial passage 49, thence out through slots 
50 into the open portion of slide valve chamber 26. 
It is to be noted that, if a gradual or modulated action of the piston is 
desired, it will suffice to exert a regular variable or traction or thrust 
on spool 39 in the desired direction and until either axial limit position 
is reached. Since the stroke of the piston 13 is adjustable both by the 
piston stroke-regulating means and by ring-like spacer 21, a variety of 
applications are possible. As well, a very precise adjustment of the limit 
positions of the unit is also possible. 
It is to be further noted that it is also possible to have a back-and-forth 
alternating movement of the piston by reciprocating the spool. In this 
function, the servo unit eliminates any hydraulic shock or cavitation, 
because of the construction and calibration of the oulet orifices which 
create a certain amount of back-pressure on the leading side of piston 13 
and very close to piston chamber 5. If the restriction was located at 
outlet port 54, the difference in the forces required to move spool 39, in 
the two opposite directions, would be increased. 
Moreover, the speed of response of the servo unit is variable due to the 
calibration of the two pairs of orifices. A gradual action can thus be 
obtained. 
It is to be further noted that the relative displacement limit means 
between the sleeve and the spool effectively prevents a too forceful or 
accidental full-stroke displacement of the piston. The piston, according 
to the provision of the elements described, can only react progressively. 
In case of a rupture in the hydraulic feed line connected to the servo 
unit, the spool will practically instantly close the orifices, thereby 
blocking the pistons. 
In service the operating pressure of the servo valve may vary from 25 to 
3000 lbs/sq. inch, or even higher. 
It is to be understood that the casing of the servo unit of the present 
invention is to be secured to a stationary support, so that piston rod 16 
may control with precision a movable member, the position of which is to 
be varied, for instance, the swashplate of a variable flow hydraulic pump.