OIL PUMP WITH SELECTABLE OUTLET PRESSURE
CROSS REFERENCE TO RELATED APPLICATION
[0001] This application claims priority to and the benefit of United States
Provisional Patent Application serial number: 61/437,365, filed 28 January 201 1, in
the name of Williamson et al., entitled OIL PUMP WITH SELECTABLE OUTLET
PRESSURE, the entire contents of which is incorporated herein by reference for all
purposes.
FIELD
[0002] This present disclosure relates generally to an oil pump assembly
including a pressure relief valve for managing the oil pump discharge pressure and
the control valve pilot pressure. More particularly, the present disclosure relates to a
pressure relief valve having a pilot valve in communication therewith having
particular application in a fixed displacement pump lubrication system in an internal
combustion engine.
BACKGROUND
[0003] It is generally known to provide an internal combustion engine including
an oil pump assembly for pumping engine oil through the engine to lubricate the
engine components through various lubrication channels (also generally known as
passageways and collectively referred to as the engine gallery). It is also known to
provide the oil pump assembly with a device to regulate the oil pump pressure. It is
generally know to regulate the discharge pressure during engine operation to satisfy
the engine's oil pressure limits and to attempt to provide energy management to the
oil pump.
[0004] Pumps for incompressible fluids, such as oil, are often either gear
pumps or vane pumps. In environments such as automotive engine lubrication
systems, these pumps will operate over a wide range of speeds, as the engine
operating speed changes, resulting in the output volume and the output pressure, as
the output of these pumps is generally supplied to a lubrication system which can be
modeled as a fixed size orifice, of the pumps changing with their operating speed.
Generally, an engine requires the lubrication oil pressure to increase from a
minimum necessary pressure level to a maximum necessary pressure level as the
engine operating speed increases, but the maximum necessary oil pressure is
generally obtained from the pumps well before the engine reaches its maximum
operating speed. Thus, the pumps will provide an oversupply of lubrication oil over a
significant portion of the engine operating speed range. Known systems employ an
oil pump, driven by the engine, for ensuring sufficient circulation of oil through the
engine. While a deprivation of oil can result in damage to engine components, overpressurized
oil is also undesirable. For example, too high an oil pressure can
destroy paper filter elements.
[0005] To prevent over-pressurized oil, it is generally know for the lubrication
system to include a pressure relief valve. To control this oversupply, and the
resulting over pressure which could otherwise damage engine components, constant
displacement pumps in such environments are typically provided with a pressure
relief valve which allows the undesired portion of the oversupplied oil to return to an
oil sump or tank or back to the inlet port of the pump so that only the desired volume,
and hence pressure, of fluid is supplied to the engine. The pressure relief valve is
connected with the oil pump and engine to vent oil back into the oil sump (i.e., to the
oil pump's suction side) when the oil pressure reaches a preset limit. One known
type of pressure relief valve is disclosed in U.S. Pat. No. 6,1 16,272, wherein the
pressure relief valve is integrated into the oil pump. The pressure relief valve
includes a piston positioned within a cylindrical bore and the piston is biased in one
direction by a spring. Pressurized oil from the oil pump outlet is supplied to the side
of the piston opposite the spring and forces the piston against the spring. As the
engine rotates faster, the oil pump also rotates faster and works harder and the oil
pressure increases. As the oil pressure increases, the piston in the oil pressure
relief valve moves against the spring and within the bore to a point where vents on
the edges of the piston allow oil to escape back to the sump or pump. With this type
of conventional oil pressure relief valve, the oil pump outlet pressure is used to
determine when the oil pressure relief valve will open to internally by-pass the high
pressure oil from the discharge side of the oil pump back to the suction side of the oil
pump. A typical oil pressure relief valve of this type would be set to open at a preset
pressure level appropriate for the particular engine and application.
[0006] Although such a conventional oil pressure relief valve is simple and
reliable, the oil pump's power consumption is relatively high as it works to increase
the oil pressure to the preset pressure level even though a lower oil pressure may be
adequate to provide satisfactory lubrication of the engine components. A high power
consumption by the oil pump equates to reduced fuel efficiency, which is a
disadvantage. In one known application, an oil pressure relief valve for use in the
lubrication system of an engine is controlled by both pump outlet pressure and by a
pilot pressure applied to the opposite side of the piston in the pressure relief valve.
The action of the pilot valve reduces the startup pressure spikes associated with
known pilot-operated valves, while also permitting a fuel economy benefit. There
long remains a need to continue to improve the fuel efficiency of the engine and its
associated components and the vehicle. Several examples of these known systems
include the systems disclosed in U.S. Patent Application publication numbers
2007/0231 161 and 2010/0028717 and U.S. Patent Number 7,775,503, the
disclosures of which are incorporated herein.
SUMMARY
[0007] In one exemplary embodiment there is disclosed a pressure relief valve
system for use in a fluid lubrication system, such as in an internal combustion engine
having an oil pump for circulated the fluid (oil) throughout the lubrication system.
The pressure relief valve system includes a pressure relief valve including a housing
having a bore having a single piston therein and a pressure relief spring for biasing
the piston in a first direction in the bore. The pressure relief valve further includes an
inlet port for admitting a fluid from a high pressure side of the fluid lubrication system
into the bore to one side (e.g., high pressure) of the piston to move the piston
against (i.e., opposite) the force of the pressure relief spring, and an outlet port for
expelling the fluid from the bore once the piston has been moved against the
increasing spring force to put the inlet port in communication with the outlet port.
The pressure relief valve further includes, in one embodiment, a pilot valve pressure
inlet port for admitting fluid into the bore of the pressure relief valve and applying the
pilot valve pressure to the piston in a direction opposite the fluid pressure from the
inlet port.
[0008] In one exemplary embodiment the pressure relief valve system further
includes a pilot valve having a pilot housing having a pilot bore having a pilot piston
and a pilot spring received therein for biasing the pilot piston in a first direction within
the pilot bore. The pilot valve further includes a pilot inlet port for admitting a fluid
from a high pressure side of the fluid lubrication system into the pilot bore to one side
of the pilot piston to move the pilot piston against the force of the pilot spring; a first
pilot outlet port for expelling the fluid from the high pressure side of the fluid
lubrication system from the pilot valve and a second outlet port for expelling the fluid
from the high pressure side of the fluid lubrication system from the pilot valve.
[0009] The pilot valve further includes second pilot piston movable within the
first pilot piston and also biased by the pilot spring in the first direction. The first pilot
piston includes a passage for admitting the fluid from the high pressure side of the
fluid lubrication system to the second pilot piston such that the first and second pilot
pistons will move against the force of the pilot spring. The pressure relief valve
system further includes, in one embodiment, a control member having an inlet and
first and second outlets wherein the inlet receives fluid from the first outlet port of the
pilot valve, the first outlet of the control member expels the fluid from the pressure
relief valve system to a reservoir and the second outlet of the control member
supplies the fluid to the pilot inlet port in the pressure relief valve. In one
embodiment, the control member is selectively operated by a signal for switching the
inlet port of the control member to communicate with one of the first and second
outlet ports of the control member. In one particular embodiment, the first and
second pistons of the pilot valve are ported so that when the control member is
activated to have the second outlet of the control member in communication with the
pilot valve inlet port of the pressure relief valve and as the oil pump speed continues
to increase, any oil pump pressure variation with be fed back to the pilot valve where
in a first position in which the oil pump pressure is temporarily too high, the first and
second pistons are arranged to have the feedback from the pressure relief valve to
be expelled to the reservoir and a in a second position, in which the oil pump
pressure is temporarily too low, the first and second pistons are arranged to apply oil
pump discharge pressure to the pilot valve input of the pressure relief valve to force
the pressure relief valve in the closing direction and to raise the oil pump outlet
pressure.
BRIEF DESCRIPTION OF THE DRAWINGS
[0010] Fig. 1 is a diagrammatic view of an illustrative example of a first
embodiment of the oil pump system with a selectable outlet at a first position;
[0011] Fig. 2 is a diagrammatic view of the oil pump system with a selectable
outlet of Fig. 1 at a second position.
[0012] Fig. 3 is a diagrammatic view of the oil pump system with a selectable
outlet of Fig. 1 at a third position.
[0013] Fig. 4 is a diagrammatic view of the oil pump system with a selectable
outlet of Fig. 1 at a fourth position.
[0014] Fig. 5 is a diagrammatic view of the oil pump system with a selectable
outlet of Fig. 1 at a sixth position.
[0015] Fig. 6 is a diagrammatic view of the oil pump system with a selectable
outlet of Fig. 1 at a seventh position.
[0016] Fig. 7 is a graph of Discharge Pressure versus Oil Pump Speed
identifying the energy savings obtained by the oil pump system with a selectable
outlet of Fig. 1.
[0017] Fig. 8 is a diagrammatic view of an illustrative example of a second
embodiment of an oil pump system with a selectable outlet at a first position;
[0018] Fig. 9 is a diagrammatic view of an illustrative example of a third
embodiment of an oil pump system with a selectable outlet at a first position;
[0019] Fig. 10 is a diagrammatic view of an illustrative example of a fourth
embodiment of an oil pump system with a selectable outlet at a first position; and
[0020] Fig. 11 is a diagrammatic view of an illustrative example of a fifth
embodiment of an oil pump system with a selectable outlet at a first position.
DETAI LED DESCRI PTION
[0021] Referring to all of the Figures in general, there is shown a schematic
view of a pump system 1 includi ng a pressure control system 10 and a pressure
relief valve system 100 of the pressure control system for such a pump system 1 is
shown in FIG . 1. The pump system 1 includes a sump or reservoir 2 which is
schematically shown toward the bottom and a working fluid is to be pumped by the
oil pump 3 from the reservoir 2 . The pump 3 may be a variable displacement type
pump with a control feature which can alter the displacement of pump 3 . However,
as will be understood by those of skill in the art, the pump 3 may be a fixed
displacement pump in which the pressure relief valve as shown is provided and
whose operating point or pressure relief valve setting can be set as desired. The oil
pump 3 is driven by the engine or other device such as an electric motor (not shown)
and when driven by the engine, the speed of the oil pump 3 varies as the engine
speed varies. As well understood in the art, as the oil pump 3 speed increases so
does the discharge pressure of the oil pump 3 .
[0022] Referring in particular to FIG . 1, the pump system 1 having a pressure
control system 10 is shown. The pressure control system includes a pressure relief
valve 00, a pilot valve 200 and a control member or solenoid valve 400 arranged as
shown. The control member 400 is preferably a two state valve of any known or
appropriate type such as a spool or ball valve that is operated by a solenoid 400 or
any other known or appropriate controller that is appropriately capable of receiving a
signal for being operated between the two states.
[0023] The system in FIG. 1 is shown in a first position in which the engine
and the oil pump 3 are not operating as represented point 1 on the graph of FIG . 1.
In this state, the control member or solenoid 400, which is preferably controlled by
the engi ne control module (or ECM, not shown) or another control module that
communicated with the ECM, is positioned in a first or ON position as shown. In this
first position , the two state valve of the control member 400 is positioned as shown in
FIG. 1.
[0024] The pressure relief valve 100 has an input 101 that receives the
discharge (or output or outlet) oil pressure from the pump 3 and an outlet 102 that
communicates or expels oil from a chamber or bore 103 in the pressure relief valve
100 to the pump 3 . The output 104 is to the reservoir 2 which goes back to the
pump 3 . The pressure relief valve 100 has a single piston member 10 that is
biased by the pressure relief valve spring 120 in a direction toward the oil pump input
101 to the pressure relief valve 100. The output or outlet 10 1 of the oil pump 3 is
applied to a first side of the pressure relief piston 110. The pressure relief valve 100
has a second or pilot input/output 104 on a second or opposite side of the pressure
relief valve piston and which works in addition to the pressure relief valve spring 120
to bias the pressure relief valve 100 toward the closed position as shown in FIG. 1.
[0025] The pilot valve 200 has a first input P therein. The pilot valve 200
includes a first piston 210 having one side receiving the force of the fluid from the
input P. The first piston 210 is biased toward the inlet P by the pilot spring 220
located in the pilot bore 213 in the housing of the pilot valve 200. The input P, in
FIG. 1 is the discharge pressure from the oil pump 3 . The first pilot piston 210 is
designed to allow input P to be communicated and/or expelled to a first pilot outlet or
output A. Output A communicates with the two state valve of the control member
400 (i.e., the OFF side of the solenoid control member. Thus if the control member
400 is in the ON position, the output A (in the position shown this is the same as inlet
P) is sealed at the control member 400 and is not further communicated to the
pressure relief valve 100. As can be readily seen from FIG. 1, when the solenoid
control member is in the ON position, the control member 400 does not
communicate the output A of the pilot valve 200 to the second or pilot input/output
104 of the pressure relief valve 100. However, in FIG. 1, it should be noted that with
there being no discharge pressure, a second pilot piston 240 is also biased toward
the pilot inlet P within the first pilot piston 210 and allows the inlet P to be
communicated to the piston 210 and through the hole 205 in the top to the top end of
the second piston 240 as well as past the piston 2 10 through the passage 206 to the
chamber 208, around the second piston 240 to the passage 209 in the piston 210
and to the outlet A. Now, as the engine is started and the engine speed increases so
does the oil pump 3 speed and the system 1 moves from the first point 1 to the
second point 2 on the chart and the system and its components move to the
positions shown in FIG. 2 .
[0026] In FIG. 2 , the oil pump 3 speed has increased and so too has the
discharge pressure applied to the pressure relief valve 100. Accordingly, the
pressure relief piston 110 has moved from the closed position 1 of FIG. 1 to a
second closed position 2 of FIG. 2 in which the increased pressure at the input 101
to the pressure relief valve 100 has moved the pressure relief piston 110 against the
force of the pressure relief valve spring 120. The solenoid control member 400
remains in the ON position such that the pilot valve remains 200 disconnected from
the pressure relief valve 100. It should also now be noted that with the discharge
pressure increase, the inlet pressure at the inlet P acts against the second pilot
piston 240 to move it down within the first pilot piston 210 against the pilot spring
220. As should be noted, the pressure relief valve 100 in FIG. 2 is about to open
and as the pump 3 speed increases the components of the system move to the
position 3 of the chart as shown in FIG. 3 .
[0027] In FIG. 3 , the oil pump 3 speed has increased and so too has the
discharge pressure at 1010 being applied to the piston 110 of the pressure relief
valve 100. Accordingly, the pressure relief piston 0 has moved from the closed
position of FIGs. 1 and 2 to an open position 3 of FIG. 3 in which the increased
pressure at the input 101 to the pressure relief valve 100 has moved the pressure
relief piston 1 0 against the force of the pressure relief valve spring 120 to the point
where now the input 10 1 to the pressure relief valve 100 is communicated past the
pressure relief piston 120 fluid is expelled to the pressure relief output and back to
the reservoir 2 and oil pump 3 and the control member 400 remains switched to the
ON position such that the two way valve remains closed. The pilot valve 200
remains in the same position as in FIG. 2 such that the output A of the pilot valve
200 remains connected to the OFF position of the two way valve of the control
member 400. As shown in the chart, with the opening of the pressure relief valve
100, the discharge pressure now goes up much more slowly as the pump speed
increases with the engine speed until in the next position 4 on the chart, the control
member is switched to the OFF position as shown in FIG. 4 .
[0028] As the speed of oil pump 3 has stayed constant but the discharge
pressure has increased significantly, due to the control member 400 bei ng switched
to the OFF position and the output A of the pilot valve 200 being applied to the pilot
input/output 104 of the pressure relief valve 100. With the increased discharge
pressure (point 4 on the chart), the pressure relief piston 100 remains in the open
position , similar to FIG. 3 . and the input to the pressure relief valve 101 is
communicated past the pressure relief piston 110 so fluid is expelled to the pressure
relief output 102 and back to the oil pump 3 . With the increased discharge pressure,
the second piston 240 of the pilot valve 200 is forced further against the pilot valve
spring 220, due to the fluid passing through the passage 205 and forcing against the
end of the second piston 240, such that the second piston 240 blocks the passage
206 and cuts off the input P from the chamber 208 thereby preventing it from
reaching the output A of the pilot valve 200 such that the output A becomes fixed
and the output A of the pilot valve 200 remai ns connected to the OFF position of the
two way valve of the control member 400 and is applied to the pilot input/output 104
of the pressure relief valve 100. As shown in the chart in the figures, with the
switching of the control member 400 by the ECM, control module or other controller,
the discharge pressure increases and the pressure relief system 1 achieves a self
correcting feedback control system. In this position, the pilot valve 200 remai ns near
its center position and the pilot valve acts like a 'potential divider' to hold the output
'A' pressure between the inlet 'P' pressure and the and pressure T (i.e. , where the
hydraulic resistances electrical resistances) which is communicated to the
reservoir 2 at the second pilot output. The pilot outlet 'A' pressure reduces from
point 4 on the chart towards poi nt 5 on the chart as the pump 3 speed and flow
increases and the pressure relief valve 100 is required to open more to recirculate
more (excess) oil fluid flow. In this embodiment, it should be understood that
pressure corrections can now be more easily and efficiently made as shown in FIGs
5-7 and along the chart from points 4 to 5 as indicated at points 6 and 7 .
[0029] In FIG . 5 , the oil pump 3 speed has increased but the discharge
pressure has stayed substantially constant at the pilot valve 200 setting . The
solenoid control member 400 remains switched to the OFF position and the output A
of the pilot valve 200 remains applied to the pilot input/output 104 of the pressure
relief valve 100. However, as the pump 3 speed increases, the pressure at the first
pilot valve outlet A reduces as the pump 3 flow increases and the pressure relief
valve 100 is required to open more to recirculate the excess flow. With the reduced
outlet pressure A, the discharge pressure at inlet P of the pilot valve 200 becomes
greater than the outlet pressure A and the second pilot valve piston 240 is moved
further against the pilot valve spring 220 until the outlet pressure A is put in
communication with the outlet T as shown by the added arrows in FIG. 5 across the
solenoid control member 400 and across the pilot valve 200. Accordingly if there is a
pressure increase in the engine, such as shown at point 6 on the chart, the
discharge pressure signal increases and the second pilot valve piston 240 in the pilot
valve 200 moves to communicate output A to output T and the pressure relief system
1 opens further and the pressure relief system 1 returns to an equilibrium on the line
4-5.
[0030] In FIG. 6 , the pressure relief system 1 is now shown at point 7 on the
chart where there is a sudden pressure drop in the engine (or elsewhere) causing a
drop in the discharge pressure supplied to inlet P to the pilot valve 200. In this
instance, the second piston 240 of the pilot valve 200 is biased to cause the inlet P
to be put back in communication with the outlet A which is then communicated to the
solenoid control member 400. Since the solenoid control member 400 remains in
the OFF position and the two way valve is located so the outlet A is communicated to
the pilot input/output 104 of the pressure relief valve 100 causing the piston 110 of
the pressure relief valve 100 to move towards the closed position and reducing the
recirculating fluid flow going to the oil pump 3 causing flow to the engine to increase
in pressure and moving from point 7 on the chart back to the equilibrium line 4-5.
[0031] FIG. 7 shows a representation of the energy potentially saved at
low/medium speeds where high pressure is not required to be supplied to the
engine. It also shows the equilibrium line 4-5 which provides additional potential
efficiency and energy savings along with the other benefits noted herein.
[0032] In FIG. 8 , a second embodiment of the pressure relief system 11 is
shown wherein an oil filter (20) is shown after the oil pump 3 and the pressure relief
valve piston 110 is balanced against the oil pump discharge pressure 101 by having
an extension member 112 and a second piston 113 located in a second chamber
14. In this embodiment, the main gallery pressure is supplied to the inlet P of the
pilot valve 200 such that the pilot valve 200 now responds to the main gallery
pressure instead of directly to the oil pump 3 output pressure as in the earlier
embodiment. The main gallery pressure P is also applied to the pressure relief valve
100 at the inlet 1 5 which is communicated to the chamber 14 and the top of the
second piston 13 such that the pressure relief valve 300 is responsive to the
pressure P (main gallery pressure) supplied through the inlet 115. As shown in the
chart, the control of the pressure relief system 11 of FIG. 8 remains similar to the first
embodiment but determined by the Gallery Pressure P regardless of the position of
the two way valve of the control member 400.
[0033] In FIG. 9 , a third embodiment of the pressure relief system 12 is shown
very similar to the fist embodiment of FIG. 1 except wherein an oil filter (20) is added
after the oil 3 pump similar to the second embodiment of FIG. 8 . In FIG. 9 , the
pressure relief valve piston inlet 10 1 is supplied directly by the pump 3 output
pressure and the main gallery pressure is supplied to the inlet P of the pilot valve
200 such that the pilot valve 200 now responds to the main gallery pressure P
instead of directly to the oil pump 3 output pressure to provide a mixed pressure
control system 12. As shown in the chart of FIG. 9 , the control of the pressure relief
system 12 of FIG. 9 remains similar to the first and second embodiments but it can
be seen that the pressure-speed curve is altered due to the mixed control.
[0034] Referring now to FIG. 10, a fourth embodiment of the pressure relief
system 13 is shown using a two pilot control system. A second pilot valve 500 is
added to the pressure control system 13 shown. The first pilot valve system 200
operates as a high pressure setting of the control member 400 and has its output A2
supplied to the two way valve of the OFF side of the solenoid control member 400
and the second pilot valve 500 operates as a low pressure setting of the control
member 400 and has its output A5 applied to the other of the two way valve of the
ON side of the solenoid control member. The embodiment of FIG. 10 also includes
an oil filter 20 added after the oil pump 3 and the pressure relief valve piston inlet
101 is supplied directly by the pump output pressure and the main gallery pressure is
supplied to the inlets P of the first and second pilot valves 200 and 500, respectively,
such that when the solenoid control member is ON, the first pilot valve 200 having a
low pressure setting A2 is supplied to the inlet/outlet 104 of the pressure relief valve
100 and such that when the solenoid control member is OFF, the second pilot valve
500 having a high pressure setting A5 is supplied to the inlet/outlet 104 of the
pressure relief valve 100. As shown in the chart in FIG. 10, the control member 400
is operated by the ECM or other controller so that the first or low pilot valve setting
A2 controls the line 2-3 which has become flat as compared to the earlier
embodiments and the second pilot or high control setting A5 controls along the line
4-5 as the speed of the pump 3 varies.
[0035] Referring now to FIG. 11, a fifth embodiment of the pressure relief
system 14 is shown wherein an oil filter 20 is added after the oil pump 3 and the
main gallery pressure feedback signal is applied to the input P of an alternate design
pilot valve 600 and the pressure relief valve piston inlet 101 is supplied directly by
the pump 3 output pressure. Similar to FIG 10, with its two pilot valves, in FIG. 11 the
single pilot valve 600 is configured and ported as a four port pilot control and
provides an outlet B which is supplied to the two way valve and the OFF side of the
solenoid control member 400 and represents a relatively high pressure pilot 'B'
setting for the line 4-5 in the chart of FIG. 11 and the outlet A of the pilot valve 600 is
supplied to the two way valve ON side of the solenoid control member 400 and has a
relatively low pressure pilot Ά ' setting corresponding to the line 2-3 in the chart in
FIG. 11. The pilot valve 600 no longer includes a first piston but only includes the
corresponding second piston 640 which has a top end including a hole 605 for
receiving the gallery feedback signal pressure P and a branch 606 which
communicates the same pressure P to a lower chamber 650 defined by the piston
640 and the bore of the housing of the valve 600 receiving the piston 640. A spring
620 biases the piston 640 toward the hold 605 in a manner similar to the prior
embodiment. Depending up on the position of the piston 640, one of the gallery
feedback signal pressure P and the reservoir pressure T is selectively supplied to the
outlet ports A and B.
[0036] Any numerical values recited herein or in the figures are intended to
include all values from the lower value to the upper value in increments of one unit
provided that there is a separation of at least 2 units between any lower value and
any higher value. As an example, if it is stated that the amount of a component or a
value of a process variable such as, for example, temperature, pressure, time and
the like is, for example, from 1 to 90, preferably from 20 to 80, more preferably from
I 2
30 to 70, it is intended that values such as 15 to 85, 22 to 68, 43 to 5 1, 30 to 32 etc.
are expressly enumerated in this specification. For values which are less than one,
one unit is considered to be 0.0001 , 0.001 , 0.01 or 0.1 as appropriate. These are
only examples of what is specifically intended and all possible combinations of
numerical values between the lowest value and the highest value enumerated are to
be considered to be expressly stated in this application in a similar manner. As can
be seen, the teaching of amounts expressed as "parts by weight" herein also
contemplates the same ranges expressed in terms of percent by weight. Thus, an
expression in the Detailed Description of the Invention of a range in terms of at "V
parts by weight of the resulting polymeric blend composition" also contemplates a
teaching of ranges of same recited amount of "x" in percent by weight of the resulting
polymeric blend composition."
[0037] Unless otherwise stated, all ranges include both endpoints and all
numbers between the endpoints. The use of "about" or "approximately" in connection
with a range applies to both ends of the range. Thus, "about 20 to 30" is intended to
cover "about 20 to about 30", inclusive of at least the specified endpoints.
[0038] The disclosures of all articles and references, including patent
applications and publications, are incorporated by reference for all purposes. The
term "consisting essentially of to describe a combination shall include the elements,
ingredients, components or steps identified, and such other elements ingredients,
components or steps that do not materially affect the basic and novel characteristics
of the combination. The use of the terms "comprising" or "including" to describe
combinations of elements, ingredients, components or steps herein also
contemplates embodiments that consist essentially of the elements, ingredients,
components or steps. By use of the term "may" herein, it is intended that any
described attributes that "may" be included are optional.
[0039] Plural elements, ingredients, components or steps can be provided by
a single integrated element, ingredient, component or step. Alternatively, a single
integrated element, ingredient, component or step might be divided into separate
plural elements, ingredients, components or steps. The disclosure of "a" or "one" to
describe an element, ingredient, component or step is not intended to foreclose
additional elements, ingredients, components or steps.
[0040] It is understood that the above description is intended to be illustrative
and not restrictive. Many embodiments as well as many applications besides the
examples provided will be apparent to those of skill in the art upon reading the above
description. The scope of the invention should, therefore, be determined not with
reference to the above description, but should instead be determined with reference
to the appended claims, along with the full scope of equivalents to which such claims
are entitled. The disclosures of all articles and references, including patent
applications and publications, are incorporated by reference for all purposes. The
omission in the following claims of any aspect of subject matter that is disclosed
herein is not a disclaimer of such subject matter, nor should it be regarded that the
inventors did not consider such subject matter to be part of the disclosed inventive
subject matter.
WE CLAIM:
CLAIMS
1. A pressure relief valve system for use in a fluid lubrication system in an
engine, the pressure relief valve system comprising:
a pressure relief valve including a housing having a bore having a piston and
a spring received therein, the pressure relief valve further including an inlet port for
admitting a fluid from a high pressure side of the fluid lubrication system into the bore
to one side of the piston to move the piston against the force of the spring and an
outlet port for expelling the fluid from the bore once the piston has been moved
against the increasing spring force to put the inlet port in communication with the
outlet port, the pressure relief valve further including a pilot valve pressure inlet port
for admitting fluid into the bore to apply fluid pressure on the piston in a direction
opposite the fluid pressure from the inlet port;
a pilot valve including a pilot housing having a pilot bore having a pilot piston
and a pilot spring received therein, the pilot valve further including a pilot inlet port for
admitting a fluid from a high pressure side of the fluid lubrication system into the pilot
bore to one side of the pilot piston to move the pilot piston against the force of the
pilot spring; a first pilot outlet port for expelling the fluid from the high pressure side
of the fluid lubrication system from the pilot valve and a second outlet port for
expelling the fluid from the high pressure side of the fluid lubrication system from the
pilot valve; and
a control member having an inlet and first and second outlets wherein the inlet
receives fluid from the first outlet port from the pilot valve, the first outlet expels the
fluid from the pressure relief valve system and the second outlet supplies the fluid to
the pilot inlet port in the pressure relief valve and the control member is selectively
operated by a signal for switching the inlet port of the control member to
communicate with one of the first and second outlet ports of the control member.
2 . The pressure relief valve system of claim 1 wherein the control member
includes a valve operated by a solenoid.
3 . The pressure relief valve system of claims 1 or 2 wherein the control member
includes a valve operated by a solenoid and the solenoid receives a signal from an
engine control module.
3 . The pressure relief valve system of claims 1 through 3 wherein the control
member is operated to reduce the power consumption of the oil pump by includes a
valve operated by a solenoid and the solenoid receives a signal from an engine
control module.
4 . A pump system for supplying pressurized working fluid to a device with
working fluid pressure requirements that vary with the operating speed of the device,
the pump system comprising:
a pump operated by the device such that the pump operating speed is
dependent upon the operating speed of the device, wherein the pump includes a
control feature regulating an outlet pressure of the pump;
a pressure regulating valve having a first inlet port and a second inlet port in
fluid communication with an outlet of the pump, a first outlet port in fluid
communication with a reservoir of working fluid and a second outlet port in fluid
communication with the control feature of the pump, the regulating valve having a
reciprocating spool that moves in response to pump operating speed to selectively
open and close fluid communication of the first inlet port and the second outlet port,
the regulating valve biased to close fluid communication between the first inlet port
and the second outlet port and open fluid communication between the first and
second outlet ports; and
a controller operable to interrupt fluid communication of the second inlet port
to alter outlet pressure of the pump between a first equilibrium pressure and a
second equilibrium pressure and wherein the controller is operable to allow fluid
communication with the second inlet port to manage outlet pressure maintain an
effective equilibrium discharge pressure as pump speed increases even when there
are pressure changes in the output pressure due to the device.