U.S. patent application number 11/128086 was filed with the patent office on 2005-09-15 for hydraulic filter assembly with priority valve.
This patent application is currently assigned to PTI TECHNOLOGIES, INC.. Invention is credited to Moscaritolo, Daniel K., Mouhebaty, Bijan.
Application Number | 20050199283 11/128086 |
Document ID | / |
Family ID | 31494803 |
Filed Date | 2005-09-15 |
United States Patent
Application |
20050199283 |
Kind Code |
A1 |
Mouhebaty, Bijan ; et
al. |
September 15, 2005 |
Hydraulic filter assembly with priority valve
Abstract
A filter module assembly utilizes a priority valve installed in
a manifold to allow for continuous filtration of hydraulic fluid up
to a predetermined flow value and diverts occasional high flow to a
secondary circuit. This arrangement provides both a low pressure
drop at a high flow condition and structural integrity (1,000,000
impulse cycles from 0 to 6000 psi) while at the same time reducing
the weight by as much as 50% from a conventional design
approach.
Inventors: |
Mouhebaty, Bijan; (Westlake
Village, CA) ; Moscaritolo, Daniel K.; (Thousand
Oaks, CA) |
Correspondence
Address: |
PILLSBURY WINTHROP SHAW PITTMAN LLP
725 S. FIGUEROA STREET
SUITE 2800
LOS ANGELES
CA
90017
US
|
Assignee: |
PTI TECHNOLOGIES, INC.
Oxnard
CA
|
Family ID: |
31494803 |
Appl. No.: |
11/128086 |
Filed: |
May 12, 2005 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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11128086 |
May 12, 2005 |
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10215110 |
Aug 8, 2002 |
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6908545 |
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Current U.S.
Class: |
137/115.08 |
Current CPC
Class: |
B01D 29/21 20130101;
B01D 2201/188 20130101; B01D 35/143 20130101; B01D 29/56 20130101;
F15B 21/041 20130101; B01D 35/157 20130101; Y10T 137/2592 20150401;
B01D 35/1573 20130101; B01D 35/1576 20130101; B01D 35/30 20130101;
F15B 13/022 20130101 |
Class at
Publication: |
137/115.08 |
International
Class: |
G05D 011/00 |
Claims
What is claimed is:
1. A fluid flow rate responsive valve comprising: (a) a valve body
having a first end and a second end and defining an inlet for fluid
flow through said first end, the valve body including: (i) a
plurality of first circular apertures defined through the periphery
of the valve body and disposed towards said first end so as to
define a secondary outlet; and (ii) a plurality of second circular
apertures defined through the periphery of the valve body and
disposed towards said second end so as to define a primary outlet;
(b) a piston having a first end and a second end in corresponding
relationship to the valve body's first and second ends, wherein the
piston includes a plurality of circular apertures through the
periphery thereof and a metering orifice, said piston being coaxial
with, and slidably mounted within, the valve body; and (c) a spring
disposed adjacent the piston's second end, wherein the spring is
biased to: (i) urge the piston into a first position within the
valve body to close the piston over the plurality of first circular
apertures when the flow rate of the fluid through the inlet is
below a predetermined threshold value, thereby allowing all of the
fluid to pass from the inlet through the metering orifice and to
the primary outlet; and (ii) allow the piston to move away from the
first position to expose the plurality of first circular apertures
when the flow rate of the fluid through the inlet is above the
threshold value, whereby the amount of fluid above the threshold
value is directed away from the primary outlet and through said
secondary outlet while the amount of fluid at and below the
threshold value continues to pass through the metering orifice to
the primary outlet.
2. The valve according to claim 1, wherein the spring is configured
such that the amount of exposure of the plurality of first circular
apertures is proportional to the flow rate of the fluid.
3. The valve according to claim 1, wherein the piston includes a
first cylindrical portion adjacent said first piston end and a
second cylindrical portion adjacent said second piston end, and the
first portion has a larger diameter than the second portion.
4. The valve according to claim 3, wherein the piston's plurality
of circular apertures are defined through the periphery of said
second cylindrical portion.
5. The valve according to claim 3, wherein the metering orifice is
defined through the interface between said first and second
cylindrical portions.
6. The valve according to claim 1, further including a retainer
member disposed on an underside of the piston's second end and a
spring guide disposed between said retainer and said spring.
7. The valve according to claim 1, wherein the valve body's second
end is capped off with an end fitting.
8. A fluid flow rate responsive valve comprising: (a) a valve body
having a first end and a second end and defining an inlet for fluid
flow through said first end, the valve body including a plurality
of first circular apertures and a plurality of second circular
apertures defined through the periphery of the valve body so as to
define, respectively, a secondary outlet and a primary outlet; (b)
a piston having a first end and a second end in corresponding
relationship to the valve body's first and second ends, wherein the
piston includes a plurality of circular apertures through the
periphery thereof and a metering orifice, said piston being coaxial
with, and slidably mounted within, the valve body; (c) a spring
guide disposed adjacent the piston's second end; and (d) a spring
disposed on said spring guide such that, when a fluid flow rate
through the inlet increases above a predetermined threshold value,
the piston moves relative to the valve body to allow the amount of
fluid above the threshold value to be directed away from the
primary outlet and through the secondary outlet while the amount of
fluid at and below the threshold value continues to pass through
the metering orifice to the primary outlet.
9. The valve according to claim 8, wherein the piston includes a
first cylindrical portion adjacent said first piston end and a
second cylindrical portion adjacent said second piston end, and the
first portion has a larger diameter than the second portion.
10. The valve according to claim 9, wherein the piston's plurality
of circular apertures are defined through the periphery of said
second cylindrical portion.
11. The valve according to claim 9, wherein the metering orifice is
defined through the interface between said first and second
cylindrical portions.
12. The valve according to claim 8, wherein the plurality of first
circular apertures are disposed towards the valve body's first end
and the plurality of second circular apertures are disposed towards
the valve body's second end.
13. The valve according to claim 8, wherein the valve body's second
end is capped off with an end fitting.
Description
RELATED APPLICATION DATA
[0001] This is a divisional of application Ser. No. 10/215,110,
filed Aug. 8, 2002, now U.S. Pat. No. ______.
BACKGROUND OF THE INVENTION
[0002] 1. Field of the Invention
[0003] The present invention generally relates to fluid filtration.
More particularly, the present invention relates to a filter
assembly for high pressure, high flow rate and low pressure drop
applications.
[0004] 2. Discussion of the Related Art
[0005] Fluid cleanliness and viscosity are two important properties
of hydraulic fluid in a fluid power system. Contaminants may be
supplied to the hydraulic system from sources both internal and
external to the system. The level of undesirable contaminants in
the hydraulic fluid affects the quality of system performance, as
well as the useful life of substantially all of the working
hydraulic components within a hydraulic system. All moving
components in contact with the fluid are vulnerable to wear, and
attendant premature failure if such contaminants are not removed
from the system. Consequently, proper cleaning of the fluid to
remove undesirable contaminants can significantly lengthen the life
of the system components, as well as reduce maintenance and its
attendant costs. Further, effective cleanliness control can result
in significant improvements in the overall reliability and
performance of the system.
[0006] Maintenance of a clean hydraulic fluid requires efficient
filtration. A number of methods have been utilized to control the
cleanliness of the fluid in hydraulic systems. The filters utilized
in typical cleanliness control systems must withstand high pressure
and/or high volume flow in certain applications. Consequently, such
filter arrangements are often expensive and can contribute to
related system problems.
[0007] Higher demands are made upon the hydraulic systems of
aircraft. Microscopic particles present a significant problem
because it is difficult to manufacture a filter element that is
capable of removing very small particles and at the same time has a
sufficient flow capacity and low pressure drop to meet the flow
requirements of typical aircraft systems.
[0008] The flow capacity of a filter is a function of the surface
area and micron removal rating. Aircraft have limited space and
weight requirements. It is difficult to manufacture a filter
element that is capable of removing fine particles, has a high flow
capacity, a low pressure drop, is small in size, and is rugged
enough for aircraft hydraulic systems.
[0009] For example, a filter may be interposed in line before the
load to provide full flow filtering. This method is effective in
many types of systems having relatively low fluid flow, e.g., 30
gallons per minute (gpm) or less. However, many hydraulic systems
provide relatively large flows at high pressures, often running on
the order of 400 gpm at pressures of 1000 pounds per square inch
(psi) or greater. Interposing a filter in line before the load is
often impractical in those high pressure systems with relatively
large fluid flows. Further, maintaining filters in such an
environment is generally quite expensive.
[0010] Alternately, full flow filtering may be provided after fluid
has serviced the load. In this method of filtering, a filter is
typically interposed in the return line between the load and the
sump. Although less costly than filtering systems having the filter
disposed before the load, return oil filtering can still be quite
costly. Additionally, as return line filters become dirty, they
develop back pressure. The development of back pressure can be a
problem in that a number of valving systems do not perform properly
with the application of back pressure.
[0011] An additional method of filtering disposes a filter in the
sump. By nature, these filters are coarse so as not to affect flow
of fluid to the pump. Consequently, while this method may be
effective for filtering large particles, small particles are not
effectively blocked.
[0012] Engine oil lubrication systems, which are typical of many
fluid systems, frequently include a filter assembly which has a
filter formed from a porous filter medium for removing damaging
particles from the lubricating oil utilized in the system.
Mechanical wear within the engine, the outside environment, and
contaminants accidentally introduced during normal servicing
provide a source of large particles which may plug lubricating
nozzles or severely damage parts and create excessive wear on any
surfaces relying on a thin film of the lubricating oil for
protection.
[0013] These systems typically rely upon a pump to force the oil
through the filter and then circulate the filtered oil to the
moving parts of the engine for lubrication. Oil is forced through
the filter by limited pressure developed on the upstream side of
the filter by the oil pump. The pressure required to force oil to
pass through the filter at a given rate will be greater for more
viscous or thick oils or for filters formed from finer pored filter
media, i.e., porous filter media having smaller average or mean
pore diameters.
[0014] Viscosity is a measure of the resistance of the fluid to
flow, or, in other words, the sluggishness with which the fluid
moves. When the viscosity is low, the fluid is thin and has a low
body; consequently, the fluid flows easily. Conversely, when the
viscosity is high, the fluid is thick in appearance and has a high
body; thus, the fluid flows with difficulty.
[0015] Oil is generally thicker or more viscous at low temperatures
and thus, when an engine is started and the engine parts and oil
are cold, a larger pressure is required to force the oil through
the filter than after the engine has reached operating temperature.
Since the pump frequently has limited pressure capabilities, many
systems include a bypass valve, which will open when the pressure
exceeds a predetermined value and allow oil to bypass the filter.
This results in unfiltered oil being pumped through the engine
where large particles may harm the moving parts and clog passages.
Further, the high upstream pressure developed during a cold start
may cause the lighting of a high pressure oil light, erroneously
indicating that the filter is dirty or that the lubrication system
is otherwise obstructed.
[0016] Automatic self-compensating flow control lubrication systems
for continuously supplying the requisite amount of lubricant to at
least one moving component of a drive system are known in the art.
Various applications require that fluid condition in a mechanical
system be continuously monitored and adjusted to maintain optimum
overall system performance.
[0017] Present lubrication systems of the type used, for example,
in drive systems for gas turbine engines are designed to supply a
near constant oil pressure to fixed jets in the various engine
components which require lubrication including bearing package,
gears, and the like. Systems such as this are designed to supply
the minimum flow required for the worst case. This philosophy
inevitably leads to excessive flow conditions in most other engine
operating modes. Deteriorating system conditions, such as clogging
jets, cannot be corrected and require operator attention with the
possibility of mission cancellation.
[0018] In addition to the primary flow functions of the system,
present configurations include some diagnostic and condition
monitoring provisions. However, these are mainly warning lights
and/or gauges, which require crew attention and only add to the
operator workload.
[0019] One such system is disclosed in U.S. Pat. No. 5,067,454
("the Waddington reference"). The disclosed invention relates to an
automatic self compensating flow control lubrication system. One or
more operating parameters, such as scavenge temperature, are
continuously monitored and the information provided to a computer.
The computer operates the first stage solenoid valve of a two stage
valve assembly which provides such an amount of lubricant to the
component as is necessary to maintain a predetermined value of the
operating parameter. Scavenge temperature is one such operating
parameter.
[0020] In the operation of this lubrication system, oil, or other
suitable liquid lubricant, is drawn from a reservoir by means of a
suitable pump through a replaceable filter assembly which
incorporates a controlled bypass valve which, together with the
filter assembly is an integral part of the pump assembly. The
bypass valve allows essentially dirty oil to be supplied to the
components of the drive system requiring lubrication in emergency
situations during which the filter is clogged. Alternatively, it
operates to continue flow of oil during cold weather starting when
the oil is too viscous to pass through the filter.
[0021] A computer controlling operation of the lubrication system
controls whether and when the bypass valve opens. Other similar
prior art systems open and close the bypass valve at fixed points,
which have the effect of reducing filter life. The Waddington
reference, by opening the bypass valve only when absolutely
necessary, increases filter life and life of the drive system by
reducing the time that dirty oil is supplied to the components
requiring lubrication.
[0022] U.S. Pat. No. 4,783,271 ("the Silverwater reference")
discloses a filter assembly which removes particles from a fluid
and which comprises two filters and a structure for directing the
fluid first through one filter and then through the other. Each
filter includes a porous filter medium. However, the filter medium
of the downstream filter is coarser than the filter medium of the
upstream filter, i.e., the mean pore diameter of the porous filter
medium of the downstream filter is greater than the mean pore
diameter of the porous filter medium of the upstream filter.
[0023] The filter assembly further includes a mechanism for sensing
the temperature of the fluid and a valve, which is responsive to
the temperature-sensing mechanism. The valve is arranged in
parallel with the upstream filter so that, when the fluid
temperature reaches a predetermined value as sensed by the sensing
mechanism, the valve opens, allowing the fluid to bypass the
upstream filter and flow through the coarser downstream filter. For
example, in one embodiment of the invention, the valve is open when
the fluid temperature is below the predetermined value.
[0024] With the filter assembly according to the Silverwater
reference, the fluid is always filtered, regardless of the
temperature of the fluid. When the fluid temperature increases,
e.g., approaches the normal operating temperature, and reaches a
predetermined value, as sensed by the sensing mechanism, the valve
closes, causing all of the fluid to flow through both filters.
Thus, the finer upstream filter removes all particles from the
fluid while the coarser downstream filter serves as a backup filter
in case the upstream filter is damaged or defective.
[0025] However, when the temperature of the fluid, as sensed by the
sensing mechanism, falls below the predetermined value, e.g., falls
below a predetermined lower limit when the engine is shut down, the
valve opens. Consequently, when the engine is next started, the
fluid partially bypasses the upstream filter but all of the fluid
is passed through the coarser downstream filter.
[0026] The downstream filter may frequently be physically smaller
than the upstream filter. Therefore, in order to minimize the
obstruction to flow by the downstream filter when filtering cold,
viscous oil, the downstream filter preferably has a much larger
mean pore diameter than the upstream filter. However, the mean pore
diameter of the downstream filter is nonetheless small enough that
the filtration provided by the downstream filter is sufficient to
remove any large particles which may have been introduced into the
fluid.
[0027] The size and the weight of a filter assembly are major
factors in hydraulic system design, especially in aerospace
applications. These demands, coupled with the further requirements
of low pressure drop, high flow rates and improved fatigue life at
continually increasing operating pressures, require departure from
the standard design approach in hydraulic systems.
[0028] Therefore, there is a need for an innovative approach in the
design of a high pressure hydraulic filter module, which provides
both the required performance (low pressure drop at a high flow
condition) and the structural integrity (1,000,000 impulse cycles
from 0 to 6000 psi) while, at the same time, reducing the weight by
as much as 50% from a conventional design.
BRIEF DESCRIPTION OF THE DRAWINGS
[0029] FIG. 1A illustrates a pressure filter module assembly with a
priority valve according to an embodiment of the present
invention;
[0030] FIG. 1B illustrates a return filter module assembly with a
priority valve according to an alternative embodiment of the
present invention;
[0031] FIG. 2 illustrates conventional approach utilizing two
filters;
[0032] FIG. 3A illustrates an assembly drawing of a priority valve
according to an embodiment of the present invention;
[0033] FIG. 3B illustrates a priority valve in the closed position
relative to the secondary outlet according to an embodiment of the
present invention;
[0034] FIG. 3C illustrates a priority valve in the open position
relative to the secondary outlet according to an embodiment of the
present invention;
[0035] FIG. 4A illustrates a pressure manifold housing according to
an embodiment of the present invention;
[0036] FIG. 4B illustrates a return manifold housing according to
an alternative embodiment of the present invention;
[0037] FIG. 5 illustrates a pressure filter bowl according to an
embodiment of the present invention;
[0038] FIG. 6A illustrates a filter element according to an
embodiment of the present invention;
[0039] FIG. 6B illustrates a filter media according to an
embodiment of the present invention;
[0040] FIGS. 7A-7D illustrate various views of the pressure filter
module assembly with a priority valve according to an embodiment of
the present invention;
[0041] FIG. 8A illustrates a schematic drawing of the pressure
filter module assembly with a priority valve according to an
embodiment of the present invention; and
[0042] FIG. 8B illustrates a schematic drawing of the return filter
module assembly with a priority valve according to an alternative
embodiment of the present invention.
DETAILED DESCRIPTION
[0043] Advancement in hydraulic systems in the 4000+psi operating
range requires an innovative filter design approach to meet the
high performance requirements, i.e., low pressure drop at a high
flow condition, structural integrity (1,000,000 impulse cycles from
0 to 6000 psi.), and reduced size and weight. To meet these
requirements using a standard approach would require a filter
element or elements with an excessive amount of media area. This in
turn will make the filter assembly extremely large, very heavy, and
structurally unsound, or, alternatively, require two filter
assemblies.
[0044] FIG. 1A illustrates a high pressure filter module assembly
100 that may, for example, be interposed in a line before a load to
provide full flow filtering. Filter module assembly 100 may include
a high pressure manifold 130, a disposable primary filter element
110, and a high pressure filter bowl 120 which is liquid-tightly
connected at one end to the high pressure manifold 130 and is
closed at the other end. The high pressure manifold 130 may include
a fluid inlet passage 140, a fluid outlet passage 145, a priority
valve 150, a disposable secondary filter element 115, and a high
pressure relief valve 156. In addition, filter module assembly 100
may include a prognostic and health monitoring device 160 to
measure pressure, temperature, and flow.
[0045] Under normal flow operating conditions, the flow enters the
high pressure manifold 130 through the fluid inlet passage 140. The
priority valve 150 allows the flow, for example up to 40 gpm, to
enter the primary circuit (flow through the primary filter element
110) and flow out through the fluid outlet passage 145.
[0046] During peak flow conditions when the flow demand exceeds 40
gpm, the priority valve 150 directs flow in excess of 40 gpm, for
example up to 160 gpm, to the secondary circuit (flow through the
secondary filter 115) and out through the fluid outlet passage
145.
[0047] FIG. 1B illustrates an alternative embodiment of the present
invention. A return filter module assembly 101 is also designed for
low pressure drop at a high flow condition, but is used at lower
pressure and impulse levels. The return filter module assembly 101
may, for example, be interposed in a return line between the load
and a sump. Return filter module assembly 101 may include a return
manifold 131, a disposable primary filter element 110, and a return
filter bowl 121 which is liquid-tightly connected at one end to the
return manifold 131 and is closed at the other end. The return
manifold 131 may include a fluid inlet passage 140, a fluid outlet
passage 145, a priority valve 150, and a disposable secondary
filter element 115. The return filter module assembly 101 may
include a bypass valve 155. In addition, return filter module
assembly 101 may also include a prognostic and health monitoring
device 160 to measure pressure, temperature and flow.
[0048] The high pressure filter module assembly 100 utilizes the
priority valve 150 installed in the high pressure manifold 130 to
allow for continuous filtration of the hydraulic fluid up to a
predetermined flow value (e.g., up to 40 gpm) and diverts the
occasional high flow to the secondary circuit. This approach
provides both the required performance (low pressure drop at a high
flow condition) and the structural integrity (1,000,000 impulse
cycles from 0 to 6000 psi) and, at the same time, may reduce the
weight by as much as 50% from a conventional design approach.
[0049] FIG. 2 illustrates a conventional design approach that
requires two filter assemblies combined in parallel as shown in the
schematic drawing. Two filters are required to meet the required
performance (low pressure drop at a high flow condition) and the
structural integrity (1,000,000 impulse cycles from 0 to 6000
psi).
[0050] The filter design including the priority valve 150 is based
on the observation that in certain applications, the normal flow
requirement in a system may be, for example, 40 gpm, with only
occasional peak flows up to 200 gpm. In more defined terms, it may
be that the peak flow of 200 gpm occurs during 5% of the
operational time of an aircraft and a flow up to 100 gpm occurs
less than 15% of the time. The remaining 80% of the time the flow
is no greater than 40 gpm.
[0051] Based on this understanding, the pressure filter module
assembly 100 provides continuous filtration of 40 gpm (primary
circuit) and allows for the bypassing of any excess flow, up to 160
gpm (secondary circuit), through a priority valve 150. The excess
flow is filtered through a parallel secondary filter 115. The
primary and secondary filters form a parallel combination to
provide for a lower pressure drop as compared to a series
combination of two filters.
[0052] It should be understood that the two scenarios 1) 200 gpm
(40 gpm filtered and 160 gpm bypassed), and 2) 100 gpm (40 gpm
filtered and 60 gpm bypassed) will still maintain the oil integrity
to ensure peak performance. The bypassing of the flow does not
degrade the performance of the hydraulic circuit or associated
components because of its relative short duration and secondary
filtration.
[0053] The purpose of the priority valve 150 is to guarantee that
all available flow up to a predetermined flow (e.g., 40 gpm) will
go to a primary (priority) circuit, including the primary filter
110. Any excess flow (e.g., up to 160 gpm) will be diverted to a
parallel secondary circuit. This parallel secondary flow or excess
flow is filtered through a more open higher micron rating filter
115 before the fluid exits through the outlet 145. One common inlet
140 and outlet 145 is used for both circuits eliminating the need
for additional plumbing.
[0054] The return filter module assembly 101 also utilizes a
priority valve 150 installed into a return manifold 131 that allows
for continuous filtration of the hydraulic fluid up to a
predetermined flow value (e.g. up to 40 gpm) and diverts the
occasional high flow to a secondary circuit.
[0055] FIG. 3A illustrates the priority valve 150 according to
embodiments of the present invention. Priority valve 150 includes a
valve body 300, first circular apertures 301, second circular
apertures 302, metering orifice 310, end fitting 320, piston
assembly 330 including a first cylindrical portion 332 and second
cylindrical portion 333 containing circular apertures 331, retainer
340, spring 350, and spring guide 360.
[0056] With reference to FIG. 3A and FIG. 3B, the piston assembly
330 is slidably mounted within the valve body 300, the spring 350
being biased in a first shape in contact with the spring guide 360
urging the piston assembly 330 into a first position within the
valve body 300 to close the first cylindrical portion 332 of the
piston assembly 330 over the plurality of first circular apertures
301 of the valve body 300 when the flow rate of a fluid is below a
predetermined fluid flow rate.
[0057] Furthermore, with reference to FIG. 3A and FIG. 3C, the
spring 350 being biased in a plurality of shapes in contact with
the spring guide 360 allowing the first cylindrical 332 portion of
the piston assembly 330 to move away from the first position to
allow the first cylindrical portion 332 of the piston assembly 330
to expose the plurality of first circular apertures 301 of the
valve body 300 when the flow rate of the fluid is above a
predetermined fluid flow rate, the plurality of first circular
apertures 301 of the valve body 300 then being in communication
with a first passage 306 (see FIG. 3C) to form a fluid pathway
secondary circuit, the plurality of spring 350 shapes and the
amount of exposure of the plurality of first circular apertures 301
of the valve body 300 is proportional to the flow rate of the
fluid. The exposure of the plurality of first circular apertures
301 of the valve body 300 defines the second piston metering
land.
[0058] FIG. 3B illustrates that when the priority valve 150 is
initially closed, flow is directed through the primary circuit,
from primary inlet 140 to the primary outlet 146, and the secondary
circuit is closed off. The pressure drop across the metering
orifice 310 in the piston assembly 330 is not high enough to
overcome the installed spring 350 force, therefore the piston
assembly 330 remains in the first position within the valve body
300. In this position the plurality of first circular apertures 301
in the valve body 300 are not exposed and thus the second piston
metering land (the exposure of the circular apertures 301 in the
valve body 300 by the piston assembly 330) is closed preventing
flow to the secondary circuit. All flow will be ported to the
primary circuit through the plurality of circular apertures 331 in
the second cylindrical portion 333 of the piston assembly 330 and
the second circular apertures 302 in the valve body 300.
[0059] FIG. 3C illustrates that as the flow to the primary circuit
increases, the pressure drop across the metering orifice 310 in the
piston assembly 330 overcomes the installed spring 350 force
forcing the piston assembly 330 downward away from the first
position within the valve body 300 to expose the plurality of first
circular apertures 301 in the valve body 300. This opens the second
piston metering land, and bypasses the excess flow to the secondary
circuit. If the primary flow across the fixed orifice 310 decreases
below the set gpm rating, the spring 350 bias force will close off
the secondary piston metering land to assure all the flow available
will be ported to the primary circuit through the plurality of
circular apertures 331 in the second cylindrical portion 333 of the
piston assembly 330 and the second circular apertures 302 in the
valve body 300. (Refer back to FIG. 3B.)
[0060] FIG. 4A illustrates a high pressure manifold 130 according
to an embodiment of the present invention. The high pressure
manifold 130 may be constructed from anodized titanium material
TI-6AL-4V. The use of titanium is recommended because of the filter
modules specification and performance requirements. Due to the
relatively large size, high pump discharge pressure levels and the
stringent qualification impulse requirements, titanium provides the
best strength to weight ratio over other material options.
[0061] Previous experience dictates that for high pressure systems
and severe impulse requirements (1,000,000 cycles from 0 to 6000
psi) the use of titanium is necessary to ensure the success of the
qualification while still providing a product with the least
weight. In an alternative embodiment of the present invention, the
high pressure manifold 130 may be manufactured using Precipitation
Hardened Stainless Steel bar 15-5 PH.
[0062] FIG. 4B illustrates the return manifold 131 according to an
alternative embodiment of the present invention. The return filter
manifold 131 may be manufactured using anodized 7075-T7351 aluminum
or 2024-T851 aluminum.
[0063] FIG. 5 illustrates the high pressure filter bowl 120
according to an embodiment of the present invention. The high
pressure filter bowl 120 is constructed from TI-6AL-4V. The bowl
achieves the desired fatigue life of the high pressure manifold
130. The high pressure filter bowl 120 houses the primary filter
element 110 and is removable for replacement of the primary filter
element 110.
[0064] The return filter bowl 121 (not shown) is the same size and
shape as the high pressure filter bowl 120. The return filter bowl
121 may be manufactured using anodized 7075-T7351 aluminum or
2024-T851 aluminum. The return filter bowl 121 also houses the
primary filter element 110 and is removable for replacement of the
primary filter element 110.
[0065] The high pressure filter bowl 120 and return filter bowl 121
may be installed and tightened by hand. Both filter bowls 120, 121
include a knurled friction pad for this purpose. No other
equipment, fitting, etc. is required to remove or disconnect the
bowl and its respective element for servicing/maintenance. In the
event that hand torque is not adequate for bowl removal, a
wrenching pad 510 is provided at the bottom of each bowl. This
design allows removal of the bowl with standard tools, but does not
allow over torquing. The pitch diameters of the bowl threads 520
are modified to preclude false installation of the similarly sized
and shaped pressure and return bowls. The high pressure filter bowl
120 may be secured to the high pressure manifold 130 with lockwire.
Alternatively, a more maintenance friendly locking lever can also
be provided if required.
[0066] FIG. 6A illustrates the primary filter element 110 according
to an embodiment of the present invention. Multi-layered filter
media provides optimum filtration capability. The primary filter
element 110 is a high pressure high collapse (in this case 6000
psi) filter element. Referring to FIG. 6B, the media pack assembly
600 is the core of the primary filter element 110. The media pack
600 may consist of four or more layers of porous material.
[0067] The outer layer 610, a corrosion resistant steel (CRES)
mesh, is for protection during handling. The second layer 620 is
the actual filter media that provides the filtration efficiency and
retained dirt capacity. It may consist of an epoxy modified
phenolic resin impregnated glass fiber matrix. The third layer 630
provides flow distribution and is used to support the media. All
additional layers 640 are to further support the media pack as
needed. These layers are pleated, formed into a cylinder to
maximize the filter area, and then side sealed with epoxy.
[0068] The center tube assembly (not shown) consists of a tube and
a wire mesh cylinder. The tube is a rolled and butted perforated
sheet, with the hole-pattern, thickness and material designed to
meet the required pressure drop and collapse strength (some high
pressure applications use cylinder wire "slinky"). The cylinder of
CRES wire mesh is wrapped around the center tube to prevent the
pleated pack assembly from pushing through the holes in the
perforated center tube at high differential pressure. Filter
element fittings and end caps are machined or stamped from 300
series CRES and passivated.
[0069] At assembly, the tube assembly is inserted into the media
pack assembly 600 which are in turn attached to the fitting and end
cap with a suitable adhesive. All materials and adhesives used in
the filter element assemblies have been shown through testing to be
fully effective for filtering fluids over the entire fluid
temperature range of -65.degree. F. to +275.degree. F. (i.e., in
this case MIL-PRF-83282 and MIL-PRF-87257).
[0070] FIGS. 7A-7D illustrate various views of the pressure filter
module assembly according to an embodiment of the present
invention. The envelope of the module may be as small as 23.1
inch.times.10.1 inch.times.9.95 inch. The calculated dry weight of
the pressure filter assembly may be as light as 70.0 lb. The high
pressure manifold 130 may be equipped with inlet 710 and outlet 720
sensors that allow for continuous monitoring of pressure,
temperature, and flow.
[0071] In an alternative embodiment of the present invention, the
return filter assembly (not shown) may be as small as 22.5
inch.times.8.5 inch.times.9.95 inch, and may have a lower
calculated dry weight of 48.0 lb maximum (due to the use of
aluminum for the manifold and bowl).
[0072] A system schematic of the pressure filter module assembly
100 and return filter module assembly 101 are shown in FIGS. 8A and
8B, respectively. The schematics illustrate the various flow paths
and the associated component locations. Under normal flow operating
conditions, the flow enters the manifold through the inlet port
810. The primary circuit allows flow up to 40 gpm to enter the
primary filter element 110 and flow out through a check valve 815
(which serves also as an outlet shutoff valve) to the outlet port
820.
[0073] During peak flow conditions when the flow demand exceeds 40
gpm, a priority valve 150 in the module directs flow in excess of
40 gpm up to 160 gpm, to the secondary circuit through a secondary
filter 115 and out through a common outlet port 820.
[0074] FIG. 1A and FIG. 8A illustrate the pressure filter module
assembly 100 may include a high-pressure relief valve 156 provided
downstream of the primary filter element 110 and secondary filter
element 115 to relieve the flow, up to 200 gpm, through the relief
valve outlet port 157 in case of a system problem (valve
malfunctions downstream causing potential catastrophic increase of
system pressure) downstream of the pressure filter module assembly
100.
[0075] FIG. 1B and FIG. 8B illustrate the return filter assembly
101 may include a bypass valve 155 in parallel with the primary
filter element 110 to allow bypassing of the primary flow, up to 40
gpm, to the outlet port 820 in the case of filter element
blockage.
[0076] While the description above refers to particular embodiments
of the present invention, it will be understood that many
modifications may be made without departing from the spirit
thereof. The accompanying claims are intended to cover such
modifications as would fall within the true scope and spirit of the
present invention. The presently disclosed embodiments are
therefore to be considered in all respects as illustrative and not
restrictive, the scope of the invention being indicated by the
appended claims, rather than the foregoing description, and all
changes that come within the meaning and range of equivalency of
the claims are therefore intended to be embraced therein.
* * * * *