U.S. patent number 3,685,531 [Application Number 05/080,060] was granted by the patent office on 1972-08-22 for circuit breaker.
This patent grant is currently assigned to Bertea Corporation. Invention is credited to Frank Byford.
United States Patent |
3,685,531 |
Byford |
August 22, 1972 |
CIRCUIT BREAKER
Abstract
A circuit breaker including a first orifice positionable in a
first fluid stream, a second orifice positionable in a second fluid
stream, and a valve responsive to the pressure drops across the
orifices being in a predetermined ratio for at least substantially
reducing the flow rate of the first fluid stream.
Inventors: |
Byford; Frank (Huntington
Beach, CA) |
Assignee: |
Bertea Corporation (Irvine,
CA)
|
Family
ID: |
22155003 |
Appl.
No.: |
05/080,060 |
Filed: |
October 12, 1970 |
Current U.S.
Class: |
137/101.11;
91/447; 91/421; 137/100 |
Current CPC
Class: |
F15B
20/005 (20130101); F16K 17/22 (20130101); Y10T
137/2526 (20150401); Y10T 137/2521 (20150401) |
Current International
Class: |
F16K
17/22 (20060101); F15B 20/00 (20060101); F16K
17/20 (20060101); F15b 011/08 () |
Field of
Search: |
;91/421,444,446,447
;137/98,100,101,101.11,106 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Nelson; M. Cary
Assistant Examiner: Zobkiw; David J.
Claims
I claim:
1. A circuit breaker comprising:
means defining a first orifice positionable in a first fluid stream
so that the fluid of such stream can pass therethrough and undergo
a first pressure drop;
means defining a second orifice positionable in a second fluid
stream so that the fluid of such stream can pass therethrough and
undergo a second pressure drop;
means responsive to the ratio of said pressure drops reaching a
predetermined value for at least substantially reducing the flow
rate of the first fluid stream;
means responsive to the pressure drop across at least one of said
orifices for automatically varying the area of said second orifice
to maintain the pressure drop thereacross substantially constant
over a range of flow rates therethrough;
means for correspondingly varying the area of said first orifice so
that the pressure drop thereacross is substantially constant;
and
said orifices being open during normal operation of the circuit
breaker.
2. A circuit breaker as defined in claim 1 wherein said orifices
are of substantially equal area whereby said pressure drops are
substantially equal for substantially the same flow rates of said
fluid streams, and said predetermined ratio is about one to
one.
3. A circuit breaker as defined in claim 1 wherein said means
responsive to the ratio of the pressure drops includes a shut off
valve.
4. A circuit breaker as defined in claim 1 wherein the areas of
said orifices are variable from substantially completely closed
positions to open positions.
5. A circuit breaker as defined in claim 1 wherein said means for
varying includes a slide valve, said circuit breaker including
means responsive to the pressure downstream of said second orifice
exceeding the pressure immediately upstream of said second orifice
for closing said slide valve whereby said slide valve also serves
as a check valve.
6. A circuit breaker as defined in claim 1 wherein said means
responsive to the ratio of the pressure drops includes a valve
member, said first orifice being of slightly larger area than said
second orifice whereby for equal flow rates the pressure drop
across the second orifice is greater than the pressure drop across
the first orifice, the pressure drop across the second orifice
being used to hold the valve member open whereby the valve member
need not be spring biased open.
7. A hydraulic fuse for use with a hydraulic device comprising:
means defining a supply conduit for supplying hydraulic fluid under
pressure to the hydraulic device;
means defining a return conduit for carrying hydraulic fluid away
from the hydraulic device;
means defining a supply orifice in said supply conduit through
which the fluid can flow, the flow of fluid through said supply
orifice causing a first pressure drop;
means defining a return orifice in said return conduit through
which the fluid can flow, the flow of fluid through said return
orifice causing a second pressure drop;
a valve member at least partially in said supply conduit and
movable between an open position in which the valve member leaves
the supply conduit open and a closed position in which the valve
member substantially shuts down flow through the supply
conduit;
means for applying a first force to said valve member having a
magnitude which is a function of the first pressure drop and
tending to move the valve member to said closed position;
means for applying a second force to said valve member having a
magnitude which is a function of the second pressure drop and
tending to move the valve member to said open position whereby the
valve member is controlled by said first and second pressure
drops;
reservoir means for supplying additional fluid under pressure to
said supply conduit downstream of said supply orifice; and
said reservoir means including a reservoir, a piston in said
reservoir movable in a first direction to expel the fluid in the
reservoir toward the hydraulic device, means for retarding movement
of said piston in said first direction and conduit means for
conducting the fluid from the reservoir to the supply conduit
downstream of the supply orifice.
8. A hydraulic fuse as defined in claim 7 including means for
maintaining the pressure drop across both of said orifices
substantially equal for equal flow rates to and from the hydraulic
device, said supply orifice being slightly larger in area than said
return orifice whereby for the same pressure drop supply flow can
exceed return flow.
9. A hydraulic fuse for use with a hydraulic device comprising:
means defining a supply conduit for supplying hydraulic fluid under
pressure to the hydraulic device;
means defining a return conduit for carrying hydraulic fluid away
from the hydraulic device;
means defining a supply orifice in said supply conduit through
which the fluid can flow, the flow of fluid through said supply
orifice causing a first pressure drop;
means defining a return orifice in said return conduit through
which the fluid can flow, the flow of fluid through said return
orifice causing a second pressure drop;
a valve member at least partially in said supply conduit and
movable between an open position in which the valve member leaves
the supply conduit open and a closed position in which the valve
member substantially shuts down flow through the supply
conduit;
means for applying a first force to said valve member having a
magnitude which is a function of the first pressure drop and
tending to move the valve member to said closed position;
means for applying a second force to said valve member having a
magnitude which is a function of the second pressure drop and
tending to move the valve member to said open position whereby the
valve member is controlled by said first and second pressure
drops;
second valve means responsive to the flow rate through the return
orifice for correspondingly varying the areas of said orifices so
that the pressure drops across each of said orifices will be
substantially the same over a range of flow rates when the flow
rates to and from the actuator are substantially the same; and
the valve member being downstream of the supply orifice and all of
the fluid flowing in the supply conduit to the valve member passing
through said supply orifice.
10. A hydraulic fuse as defined in claim 9 wherein said hydraulic
fuse includes biasing means for resisting the opening of said
second valve means.
11. A circuit breaker comprising:
a body having first and second fluid passages therein;
first means defining a first orifice in said first passage;
second means defining a second orifice in said second passage, said
orifices being of about the same area so that the pressure drops
across said orifices are about the same for equal flow rates;
a slide valve in said first fluid passage having first and second
sets of pressure responsive faces, each of said sets of pressure
responsive faces including generally opposed pressure responsive
faces;
first passage means for supplying fluid under pressure from
upstream and downstream of said first orifice to the opposed faces,
respectively, of said first set of pressure responsive faces with
the net effect being the urging of the slide valve toward a closed
position in which substantially no fluid can flow through said
first passage;
second passage means for supplying fluid from upstream and
downstream of said second orifice to the opposed faces,
respectively, of said second set of pressure responsive faces with
the net effect being the urging of said slide valve toward an open
position in which fluid can flow through said first passage;
a reservoir in communication with the first fluid passage
downstream of said slide valve; and
means for expelling fluid from the reservoir into the first passage
downstream of said slide valve.
12. A circuit breaker as defined in claim 11 wherein said first and
second means includes a second slide valve movable in said first
and second fluid passages to partially define said orifices and to
vary the areas thereof.
13. A circuit breaker as defined in claim 12 including means
responsive to the pressure drop across said second orifice for
controlling the position of said second slide valve to increase the
areas of said orifices in response to an increase in the pressure
drop across said second orifice and to decrease the areas of said
orifices in response to a reduction in the pressure drop across
said second orifice.
14. A circuit breaker as defined in claim 13 including resilient
means for urging said second slide valve in a direction to reduce
the areas of said orifices, said means for expelling including a
piston movable in at least one direction in said reservoir and
biasing means for retarding the movement of said piston in said one
direction.
15. A circuit breaker for use with a hydraulic device
comprising:
a supply conduit for supplying fluid under pressure to the
hydraulic device;
a return conduit for carrying fluid away from the hydraulic
device;
valve means in said supply conduit responsive to the quantity of
fluid flowing through said supply conduit exceeding by a
predetermined amount the quantity of fluid flowing through the
return conduit for closing said supply passage;
reservoir means for providing a small quantity of fluid to said
supply conduit intermediate said valve means and the hydraulic
device to thereby cause fluid flow in said return conduit to cause
opening of said valve means for start up; and
means responsive to the quantity of fluid flowing through said
return conduit being at least about equal to the quantity of fluid
flowing through the supply conduit for holding said valve means
open.
16. A circuit breaker as defined in claim 15 wherein said reservoir
means includes a reservoir, first conduit means providing
communication between said reservoir and a location in said supply
conduit upstream of said valve means, second conduit means for
providing communication between said reservoir and a location in
said supply conduit downstream of said valve means, a piston
movable in said reservoir to expel fluid therein through said
second conduit means into said supply conduit, and resilient means
for retarding the movement of said piston in a direction tending to
expel fluid from the reservoir through said second conduit means
into said supply conduit.
17. A hydraulic device comprising:
a body having first and second fluid passages therein;
a valve member movable in both of said passages to define therewith
first and second orifices of variable area in the first and second
passages, respectively;
resilient means for urging said valve member in a direction tending
to reduce the areas of said orifices; and
said valve member having first and second pressure responsive
faces, said first pressure responsive face being exposed to fluid
in said second passage upstream of said second orifice and said
second pressure responsive face being exposed to fluid in said
second passage downstream of said second orifice, said pressure
responsive faces being arranged so that the pressure drop across
said second orifice influences the position of said valve member
with an increase in the pressure drop across said second orifice
tending to move the valve member to increase the areas of said
orifices;
said valve member being positioned to define said orifices at least
during normal operation of the hydraulic fuse whereby all of the
fluid flowing downstream of the valve member passes through said
first orifice;
a shut off valve means in said first passage downstream of said
valve member and responsive to the ratio of the pressure drops
across said orifices being in a predetermined ratio for closing
said first passage;
a reservoir;
first and second conduits for connecting said reservoir to
locations in said first passage upstream and downstream,
respectively, of said shut off valve means; and
means in said reservoir at least partially responsive to a pressure
differential in said conduits for expelling fluid from the
reservoir and through said second conduit to said first
passage.
18. A circuit breaker for use with a hydraulic device
comprising:
means defining a supply conduit for supplying hydraulic fluid under
pressure to the hydraulic device;
means defining a return conduit for carrying hydraulic fluid away
from the hydraulic device;
means defining supply orifice means in said supply conduit through
which the fluid can flow, the flow of fluid through said supply
orifice means causing a first pressure drop;
means defining return orifice means in said return conduit through
which the fluid can flow, the flow of fluid through said return
orifice means causing a second pressure drop;
a valve member at least partially in said supply conduit and
movable between an open position in which the valve member leaves
the supply conduit open and a closed position in which the valve
member substantially shuts down flow through the supply
conduit;
means for applying a first force to said valve member having a
magnitude which is a function of one of the pressure drops and
tending to move the valve member to said closed position;
means for applying a second force to said valve member having a
magnitude which is a function of the other of the pressure drops
and tending to move the valve member to said open position whereby
the valve member is controlled by said first and second pressure
drops; and
means for increasing the effective areas of both of said orifice
means automatically in response to an increase in pressure drop
across at least one of said orifice means.
19. A circuit breaker as defined in claim 18 wherein said means for
increasing the effective area of said first orifice means includes
a valve member, said circuit breaker including spring means for
biasing at least one of said valve members.
20. A circuit breaker as defined in claim 18 including means for
supplying limited quantities of additional hydraulic fluid under
pressure to the hydraulic device to thereby tend to increase return
flow a limited amount.
21. A circuit breaker for use with a hydraulic device
comprising:
a first conduit for supplying hydraulic fluid under pressure to the
hydraulic device;
a second conduit for carrying hydraulic fluid away from the
hydraulic device;
a shut off valve member movable to block said supply conduit;
means for normally urging said shut off valve member in an opening
direction;
means including restricted passage means in said first and second
conduits for measuring flow in said first and second conduits;
flow summing means associated with said shut off valve member for
causing said valve member to move in a closing direction in
response to said measuring means when the flow in said first
conduit exceeds the flow in said second conduit by a predetermined
amount; and
control valve means disposed in said first and second conduits and
effective in response to small pressure differentials reflecting
increases in flow demand by said hydraulic device to increase the
flow through said circuit breaker and to maintain substantially
constant pressure differentials across the restricted passage means
as such flow through the circuit breaker is increased.
Description
BACKGROUND OF THE INVENTION
It is often necessary or desirable to provide an indication, or to
take remedial action, when a leak of predetermined magnitude
develops in a hydraulic system. To accomplish this purpose, it is
necessary to continuously monitor the condition of the hydraulic
system even through portions of such system may be remotely
located.
Leak detection is particularly important in hydraulic systems used
on aircraft. As is well known, hydraulic systems are utilized on
many aircraft to control the control surfaces of the aircraft. To
insure reliability, the systems are often redundant so that if one
system or a component thereof malfunctions, the other system or
component is operative to provide the necessary control motion.
If a leak of predetermined magnitude develops in one of the
hydraulic systems, it is absolutely essential that such system be
shutoff from the source of hydraulic fluid under pressure to
prevent complete loss of the hydraulic fluid and ultimate
destruction of the aircraft. A circuit breaker or hydraulic fuse is
utilized to accomplish this detection and shutoff function. In
order to be useful for aircraft applications, the hydraulic fuse
must be very reliable.
SUMMARY OF THE INVENTION
The present invention provides a reliable circuit breaker which
compares fluid flows to and from a device and shuts down the supply
flow if the supply and return flows reach a predetermined ratio.
The circuit breaker is usable with any liquid operated or handling
device if such device utilizes supply and return flows in a
predetermined ratio, and the hydraulic system shown and described
herein is merely illustrative. Thus, as used herein the expression
"hydraulic fuse" is not limited to a device usable only with
hydraulic oil but rather it includes devices usable with many other
liquids. In a typical hydraulic system the return flow is a
function of the supply flow if there are no leaks in the system.
For example, the supply flow and return flows to many hydraulic
components such as a balanced hydraulic actuator should be
substantially equal except for minor factors such as bulk modulus.
Thus, the difference between supply and return flows indicates the
amount of leakage in the system.
To accomplish flow measurement, the present invention provides
supply and return orifices in the supply and return conduits,
respectively. The areas of both of the orifices are known and bear
a predetermined relationship to each other. Preferably the areas of
the orifices are equal so that the pressure drops thereacross for
equal flow rates are also equal. Accordingly, the leakage of the
system is a function of the difference in the pressure drops across
the orifices.
The pressure drops across the orifices are used to control a
shutoff valve. If the difference in pressure drop exceeds a
predetermined magnitude, the valve shuts off the supply of
hydraulic fluid. The pressure drop across the supply orifice tends
to close the valve while the pressure drop across the return
orifice tends to open the valve. Accordingly, if the pressure drop
across the return orifice decreases, as it would if return flow
decreased, the system has a leak, and the valve would shut off the
supply of hydraulic fluid. The valve can advantageously take the
form of a slide valve having pressure responsive faces thereon
against which the pressure drops across the supply and return
orifices can act.
The present invention provides means for opening the shutoff valve
during start up of the system, if at that time, the shutoff valve
is closed. This function is performed by a reservoir which provides
a small quantity of fluid to the supply conduit intermediate the
shutoff valve and the hydraulic device to operate the hydraulic
device and to thereby initiate fluid flow in the return conduit.
This results in a pressure drop across the return orifice, and this
pressure drop is utilized to open the shutoff valve.
The volume of the reservoir is very small in relation to system
volume. The reservoir may contain a piston exposed to hydraulic
fluid at supply pressure upstream of the supply orifice. This
drives the piston to cause expulsion of the fluid in the reservoir
into the supply conduit. To permit recharging of the reservoir when
the fluid therein is depleted or partially depleted, biasing means
are provided to retard movement of the piston in a direction
tending to expel the fluid from the reservoir into the supply
conduit. The spring permits the reservoir to be recharged by
hydraulic fluid which is under a pressure slightly less than the
supply pressure upstream of the supply orifice. Although the
reservoir can be recharged in various different ways, the manner
disclosed herein is preferred because of its simplicity.
The areas of the supply and return orifices are difficult to
control. Preferably the supply orifice is of slightly larger area
than the return orifice so that for a given pressure drop more
fluid can flow therethrough than through the return orifice. Stated
differently, supply flow can slightly exceed return flow and this
additional supply flow can be utilized to recharge the reservoir
and to make up for minor leaks which the system can readily
tolerate. Although the supply and return orifices are described
herein as being of substantially equal area, it should be
understood that this expression encompasses a supply orifice being
of slightly larger diameter than the return orifice.
Another function of the reservoir occurs when the hydraulic device
is an unbalanced actuator. In this event, the flow input to the
actuator may be different from the flow output from the actuator,
and hence the reservoir will add to or subtract from the flow
supplied through the supply orifice to make up for the
differential.
Another problem relates to the sizing of the orifices. It is
generally desirable to maintain pressure drops in a hydraulic
system at a minimum, and this would seemingly dictate sizing of the
orifices for the desired pressure drop at maximum flow rates.
However, it the orifices are sized for maximum flow rates, the
pressure drops thereacross at low flow rates may not produce
sufficient force to operate the shutoff valve.
To overcome this problem, the present invention provides variable
area supply and return orifices. The area of the supply and return
orifices vary together so that the areas thereof are substantially
the same. The areas of the orifices vary with the pressure drop
across the return orifice with an increase in such pressure drop
resulting in increasing the areas of the orifices. In this manner,
the area of the return orifice is varied so that the pressure drop
thereacross is substantially the same over a range of flow rates.
Moreover, the area of the supply orifice is correspondingly varied
so that for a no leak condition, the pressure drop thereacross
remains substantially constant even though the supply flow rate may
change.
The variable orifice concept can be advantageously implemented by
utilizing a slide valve positionable in both the supply and return
conduits. The slide valve partially defines both of the orifices
and by moving the slide in the appropriate direction, the area of
the orifices can be increased or decreased simultaneously. This
slide valve also serves as a check valve.
The invention can best be understood by reference to the following
description taken in connection with the accompanying illustrative
drawing.
BRIEF DESCRIPTION OF THE DRAWING
FIG. 1 of the drawing is a schematic view partially in section
illustrating a preferred form of hydraulic fuse constructed in
accordance with the teachings of this invention.
FIG. 2 is a schematic view of an unbalanced actuator.
DESCRIPTION OF THE PREFERRED EMBODIMENT
FIG. 1 illustrates a hydraulic fuse 11 constructed in accordance
with the teachings of this invention. It should be understood that
FIG. 1 of the drawing is schematic and that the configuration and
construction of the components can be varied by those having
ordinary skill in the art. Moreover, elements such as seals having
no relationship to the concept of the invention have been omitted
for clarity, it being understood that such elements can readily be
provided as necessary or desired by those having ordinary skill in
the art.
The hydraulic fuse 11 is part of a hydraulic control system 13
usable to control a control surface 15 of an aircraft (not shown),
although it may be utilized in other environments. The position of
the control surface 15 is controlled by a hydraulic actuator 17
which includes a housing 19, a piston 21 and connecting linkage 23
drivingly connecting the piston and the control surface. Movements
of the piston 21 within the housing 19 are controlled by a servo
valve 25 which controls the flow of hydraulic fluid to and from the
faces of the piston 21. Of course, the actuator 17 and the servo
valve 25 can be of various designs and function in various
ways.
The servo valve 25 may include numerous control system components
such as an electrohydraulic valve, a modulating piston, etc. Fluid
under pressure is supplied from a source 29 and return fluid
returns to a sump 31.
The hydraulic fuse 11 includes a body 33 having a supply passage or
conduit 35 and a return passage or conduit 37 extending
therethrough. A slide valve 39 having lands 41 and 43 defining an
annular groove 45 therebetween is mounted for sliding movement in a
bore 47 which extends transversely between the supply passage 35
and the return passage 37. The land 41 cooperates with the supply
passage 35 to define a variable area supply orifice 49. Similarly,
the land 43 cooperates with the return passage 37 to define a
return orifice 51. The orifices 47 and 51 are of substantially
equal area with the supply orifice 49 being slightly larger in area
than the orifice 51.
The slide valve 39 has pressure responsive end faces 52 and 52a.
The face 52 and one end of the bore 47 cooperate to define a
chamber 53. A spring 55 acts between one end of the bore 47 and the
face 52 to urge the slide valve 39 in a direction tending to reduce
the areas of the orifices 49 and 51. A passage 57 provides
communication between the chamber 53 and the return conduit 37
downstream of the return orifice 51 to thereby permit fluid
pressure to act on the face 52. Although the passage 57 in the
embodiment illustrated extends through the slide valve 39, it
should be understood that this is merely for convenience of
illustration and that the passage 57 may physically take other
routes in reaching the chamber 53.
A shutoff valve 59 is mounted in a bore 61 which extends
transversely of the supply passage 35 downstream of the orifice 49.
The shutoff valve 59 has axially spaced lands 63 and 65 and
pressure responsive and faces 67 and 69. The land 63 has pressure
responsive annular faces 71 and 73 and the land 65 has pressure
responsive annular faces 75 and 77. In the embodiment illustrated,
the areas of the faces 67, 69, 71, 73, 75 and 77 are equal.
The shutoff valve 59 is controlled by the pressure drops across the
orifices 49 and 51. Thus, fluid under pressure from upstream of the
orifice 49 is supplied to the face 77 by a passage 79, and fluid
under pressure from downstream of the orifice 49 is supplied to the
pressure responsive face 71 by a passage 81. Thus, the net force as
a result of the pressure drop across the orifice 49 urges the
shutoff valve 59 toward a closed position in which the land 65
closes off a port 83.
Fluid under pressure from upstream of the return orifice 51 is
supplied to the pressure responsive and face 67 by a passage 85,
and fluid under pressure from a location in the return conduit 37
downstream of the orifice 51 is supplied to the pressure responsive
end face 69 by a passage 87. Thus, the pressure drop cross the
orifice 51 acts, in effect, on the shutoff valve 59 in a direction
tending to open the latter, i.e., to increase the area of the port
83. In this manner, the shutoff valve 59 is controlled by the
pressure drops across the supply orifice 49 and the return orifice
51.
A reservoir 89 is provided in the body 33. A passage 91 provides
communication between one end of the reservoir 89 and a location in
the supply conduit 35 upstream of the supply orifice 49. A passage
93 provides communication between the other end of the reservoir 89
and a location in the supply conduit 35 downstream of the port 83.
A piston 95 is mounted in the reservoir 89 for sliding movement
therein, and a spring 97 urges the piston downwardly as viewed in
FIG. 1, i.e., toward the passage 91.
Movement of the piston 95 upwardly as viewed in FIG. 1 by the fluid
pressure supplied through the passage 91 expels hydraulic fluid
from the reservoir 89 into the supply conduit 35 downstream of the
port 83. Similarly, under other operating conditions, hydraulic
fluid can be supplied through the passage 93 to urge the piston 95
downwardly as viewed in FIG. 1 thereby charging the reservoir. The
spring 97 is of such a strength that under certain operating
conditions the force supplied by the spring and the force exerted
by the fluid under pressure supplied through the passage 93 is
sufficient to move the piston 95 downwardly for recharging.
OPERATION
The position of the shutoff valve 59 at start up is unknown.
Moreover, the valve 59 is in equilibrium prior to start up because
no hydraulic fluid is flowing through the orifices 49 and 51.
Assuming that the shut-off valve 59 is in a position to completely
close off the port 83 at start up, fluid under pressure from the
supply conduit 35 and the passage 91 acts on the piston 95 in the
reservoir 89 to move the latter to expel hydraulic fluid through
the passage 93 and into the supply conduit 35 downstream of the
closed port 83.
The hydraulic fluid in the reservoir 89 is supplied to the actuator
17. Because the actuator 17 is a balanced actuator, this results in
a substantially equal flow of hydraulic fluid from the actuator
into the return passage 37 and through the return orifice 51. The
flow of hydraulic fluid through the return orifice 51 produces a
pressure drop which acts on the shutoff valve 59 to move the latter
to open the port 83 to permit additional fluid to be supplied to
the actuator 17. Specifically, the end face 67 is supplied with
fluid under pressure upstream of the return orifice 51 via the
passage 85, and the pressure responsive face 69 is supplied with
fluid from downstream of the return orifice 51 via the passage 87.
The net effect is a force on the valve 59 tending to open the port
83.
At start up the slide valve 39 is moved by the spring 53 to
completely close the ports 49 and 51. The pressure of the return
fluid in the return conduit 37 acting on the face 52a is sufficient
to move the valve 39 to open the orifices 49 and 51.
With fluid flowing through the orifices 49 and 51, the shutoff
valve 59 seeks a position which is a function of the pressure drops
across the orifices 49 and 51. Because the supply orifice 49 is of
slightly larger area than the return orifice 51, the flow through
the supply orifice can slightly exceed the flow through the return
orifice without making the pressure drop across the orifice 49
larger than the pressure drop across the orifice 51. This increased
flow can be utilized to recharge the reservoir 89 as the combined
effects of the pressure of the fluid from the passage 93 and the
spring 89 are sufficient to overcome the force of the fluid from
the passage 91 acting on the piston. Once the reservoir 89 is fully
charged, the flow through the orifice 49 reduces slightly until it
equals the flow through the return orifice 51. Accordingly, the
pressure drop across the orifice 49 is then less than the pressure
drop across the orifice 51 with the result that the shutoff valve
59 is held in the fully open position.
If the actuator 17 requires increase quantities of fluid, the flow
through the supply passage 35 and the return passage 37 increase.
This produces an increased pressure drop across the return orifice
51 with the result that the slide valve 39 is moved to increase the
areas of the orifices 49 and 51 until the predetermined pressure
drop across the return orifice 51 has been reestablished.
Similarly, if the flow through the return orifice 51 decreases, the
slide valve 39 is repositioned to reduce the size of the orifices
49 and 51 to reestablish the predetermined desired pressure drop
across the orifice 51. Thus, the slide valve 39 maintains the
pressure drop across the return orifice 51 at a preset value over a
relatively wide range of flow rates.
Because the supply orifice 49 is of a larger area than the return
orifice 51, minor leaks in the system 13 can be tolerated without
causing shut down of the system. If a leak, for example, in the
supply conduit 35 downstream of the passage 93 exceeds the minor
amount permissable, the pressure drop caused thereby will permit
the piston 95 to supply the needed makeup. In this event the flow
through the orifices 49 and 51 will be substantially equal and
substantially no effect will be felt on the slide valve 39 or the
shutoff valve 59.
However, the reservoir 89 is of relatively small volume and the
fluid therein would be quickly exhausted by a major leak. Once the
fluid therein was exhausted, a continuing leakage would result in a
reduction in the flow rate through the return orifice 51. However,
because the demand of the actuator 17 still exists, flow through
the supply orifice 49 would continue and would exceed the flow
through the return orifice 51. The result is that the pressure drop
across the supply orifice 49 would exceed the pressure drop across
the return orifice 51, and this would cause the shutoff valve 59 to
move in a direction tending to close off the port 83. Specifically,
the relatively high pressure acting in the face 77 would cause
movement of the shutoff valve 59 to close the port 83.
The reduction in flow through the return orifice 51 would also
result in repositioning of the slide valve 39 to reduce the areas
of the orifices 49 and 51. However, in normal operation the shutoff
of the supply flow through the conduit 35 would be accomplished by
the shutoff valve 59. With the shutoff valve 59 in the closed
position, there is no flow through the supply and return passages
and the slide valve 39 is moved by the spring 55 to completely
close the orifices 49 and 51. The slide valve 39 also serves a
check valve in that it closes the orifices 49 and 51 if pressure
downstream of the return orifice 51 equals or exceeds the pressure
upstream of the return orifice.
In the embodiment illustrated in FIG. 1, the actuator 17 is a
balanced actuator, i.e., one in which the return flow from the
actuator equals the supply flow to the actuator excluding the
relatively minor effects of bulk modulus. In an unbalanced
actuator, there is some disparity between the supply flow to the
actuator and the return flow from the actuator, although these
flows may be considered as substantially equal. FIG. 2 shows an
unbalanced actuator 101 which includes a housing 103, a piston 105
and a connecting rod 107 for drivingly connecting the piston to the
control surface 15.
The piston 105 has opposed faces 109 and 111. It is apparent that
with fluid at supply pressure being supplied to the face 109 to
move the piston to the right as viewed in FIG. 2 the return flow
will exceed the supply flow. This is because the connecting rod 109
reduces the volume of the cylinder 103 on the left side of the
piston 105. Conversely, with fluid under pressure being supplied to
the face 111 to move the piston 105 to the left, supply flow will
exceed the return flow.
The reservoir 89 compensates for the disparity in supply and return
flows caused by the differential actuator 101. Thus, with the
actuator 101 substituted for the actuator 17 of FIG. 1, the
reservoir 89 supplies additional fluid when the piston 105 is being
driven to the left and absorbs excess fluid supplied through the
orifice 49 when the piston 105 is driven to the right.
Specifically, when a high demand for fluid is made, there is a
pressure drop intermediate the port 83 and the servo valve 25 which
permits the pressure in the conduit 91 to move the piston 95
upwardly to expel fluid therefrom to supply the excess needed by
the unbalanced actuator. Should the actuator then be moved in the
reverse direction so that return flow exceeds supply flow, there is
a pressure increase downstream of the port 83 because the
requirements of the actuator are fully met thereby permitting the
piston 95 to be driven downwardly to recharge the actuator. Thus,
the piston 95 breathes in unison with the unbalanced actuator 101.
The volume of the reservoir should equal the differential volume of
the unbalanced actuator 101 plus a slight excess volume to allow
for bulk modulus and other effects that may cause inadvertent
bottoming of the piston 95 in the reservoir 89.
Although an exemplary embodiment of the invention has been shown
and described, many changes, modification, and substitutions may be
made by one having ordinary skill in the art without necessarily
departing from the spirit and scope of this invention.
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