U.S. patent application number 11/516006 was filed with the patent office on 2007-01-04 for exhaust gas recirculation valve having a rotary motor.
Invention is credited to Gary Michael Everingham, Kirk Ivens.
Application Number | 20070001136 11/516006 |
Document ID | / |
Family ID | 33554998 |
Filed Date | 2007-01-04 |
United States Patent
Application |
20070001136 |
Kind Code |
A1 |
Everingham; Gary Michael ;
et al. |
January 4, 2007 |
Exhaust gas recirculation valve having a rotary motor
Abstract
An exhaust gas recirculation valve is provided. The exhaust gas
recirculation valve has a base, a spring biasing the valve closed,
and an actuator including a rotary motor and a linearly
displaceable shaft that is coupled to the motor's rotor. The valve
includes a valve member and valve seat disposed within a fluid
conduit, and the spring is disposed between the actuator and the
valve.
Inventors: |
Everingham; Gary Michael;
(Chatham, CA) ; Ivens; Kirk; (Chatham,
CA) |
Correspondence
Address: |
SIEMENS CORPORATION;INTELLECTUAL PROPERTY DEPARTMENT
170 WOOD AVENUE SOUTH
ISELIN
NJ
08830
US
|
Family ID: |
33554998 |
Appl. No.: |
11/516006 |
Filed: |
September 5, 2006 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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10759230 |
Jan 20, 2004 |
|
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11516006 |
Sep 5, 2006 |
|
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60440857 |
Jan 17, 2003 |
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Current U.S.
Class: |
251/77 ;
251/129.15 |
Current CPC
Class: |
F02M 26/54 20160201;
F16K 31/047 20130101 |
Class at
Publication: |
251/077 ;
251/129.15 |
International
Class: |
F16K 31/44 20060101
F16K031/44 |
Claims
1. An exhaust gas recirculation valve, comprising: a base including
a fluid conduit extending between first and second ports; a valve
member disposed within the fluid conduit, the valve member being
configured from a closed to an open position by linear displacement
of the valve member; a valve shaft having a first end fixed to the
valve member; a linear actuator including a rotary motor, the
linear actuator positioned to exert an actuator force on the valve
shaft to displace the valve shaft in a first direction; and a valve
spring disposed between the actuator and the valve shaft, the valve
spring being positioned to exert a spring force on the valve shaft
in a second direction opposite the first direction, the spring
force being sufficient to back drive the linear actuator.
2. The-exhaust gas recirculation valve of claim 1, further
comprising:. a pintle assembly including the valve shaft and a
moving member of the valve member; and a spring cup connecting the
spring with the valve shaft, wherein a preload on the spring is
greater than a force represented by: (mass of pintle assembly+1/2
mass of valve spring+mass of spring cup)*(expected acceleration
load on exhaust gas recirculation valve).
3. The exhaust gas recirculation valve of claim 2, wherein the
expected acceleration load on the valve is 13 G.
4. The exhaust gas recirculation valve of claim 1, wherein the
motor is a synchronous motor.
5. The exhaust gas recirculation valve of claim 1, wherein the
actuator includes a member coupled to the motor's rotor and the
member is disposed adjacent to a second end of the valve shaft.
6. The exhaust gas recirculation valve of claim 5, wherein the
member includes a disc-shaped end, the valve shaft includes a
curved end, and wherein when the valve is configured in the open
position, the curved surface is in contact with the member's
end.
7. The exhaust gas recirculation valve of claim 1, wherein the
spring is a linear spring.
8. The exhaust gas recirculation valve of claim 7, wherein the
valve shaft includes a flange and the spring is disposed between
the flange and the valve member.
9. The exhaust gas recirculation valve of claim 8, the exhaust gas
recirculation valve further including a bracket having a first end
secured to the base and a second end, wherein the actuator is
disposed above the bracket and the spring is disposed between the
bracket first and second ends.
10. A method for failsafe operation of an exhaust gas recirculation
valve, comprising the steps of: providing a valve portion including
a valve member engaged with a valve seat; providing a linear
actuator for displacing the valve member, wherein the actuator is
powered by a rotary motor; providing a linear compression spring
for exerting a spring force on the valve member; actuating the
linear actuator to displace the valve member from a first position
to a second position; and returning the valve member from the
second position to the first position by back driving the rotary
motor with the linear compression spring.
11. The method of claim 10, wherein the linear actuator has a
thread pitch, and wherein the step of returning the valve member
from the second position to the first position by back driving the
rotary motor with the linear compression spring further comprises
backdriving the rotary motor through the thread pitch.
12. The method of claim 10, wherein the second position corresponds
to a closed valve position.
13. The method of claim 10, wherein the step of providing a linear
actuator for displacing the valve member includes providing an
actuator having an actuator shaft, the rotary motor displacing the
shaft to first and second shaft positions corresponding
respectively to the shaft being decoupled from the valve member and
coupled to the valve member.
14. The method of claim 13, wherein the providing a linear actuator
includes providing a disc-shaped element disposed at the end of the
shaft.
15. The method of claim 13, wherein the actuating step includes
measuring a displacement of the shaft.
16. The method of claim 15, wherein the contacting step includes
detecting an absence of displacement of the shaft.
17. The method of claim 16, wherein the detecting an absence of
displacement for a period of 100 milliseconds.
18. The method of claim 13, wherein the actuator includes a sensor
for determining the position of the shaft and the actuator includes
a rotation-to-displacement coupling between the shaft and the
motor's rotor.
19. The method of claim 13, wherein the motor has an axis of
rotation and the valve portion includes a stem having a
longitudinal axis that is substantially parallel to the axis of
rotation, the stem having a first end that is fixed to the valve
member and a second end adapted for being in contact with the
shaft.
20. The method of claim 13, wherein the shaft is decoupled from the
spring.
Description
PRIORITY
[0001] This application is a continuation application of U.S.
application Ser. No. 10/759,230, filed Jan. 20, 2004, entitled
"Exhaust Gas Recirculation Valve Having a Rotary Motor," by Gary
Everingham and Kirk Ivens, which is hereby incorporated by
reference in its entirety, which claims the benefit of U.S.
Provisional Application Ser. No. 60/440,857 entitled "Synchronous
Motor Exhaust Gas Recirculation Valve" by Gary Everingham and Kirk
Ivens and filed on Jan. 17, 2003, which provisional application is
hereby incorporated by reference in its entirety. The parent U.S.
application Ser. No. 10/759,230 is related to U.S. application Ser.
No. 10/759,229 ("Exhaust Gas Recirculation Valve Having a Rotary
Motor") filed on Jan. 20, 2004, and to U.S. application Ser. No.
10/759,231 ("Exhaust Gas Recirculation Valve Having a Rotary
Motor") filed on Jan. 20, 2004.
BACKGROUND OF THE INVENTION
[0002] Controlled engine exhaust gas recirculation ("EGR") is a
known technique for reducing oxides of nitrogen in products of
combustion that are exhausted from an internal combustion engine to
atmosphere. A known EGR system employs an EGR valve that is
controlled in accordance with engine operating conditions to
regulate the amount of engine exhaust gas that is recirculated to
the induction fuel-air flow entering the engine for combustion so
as to limit the combustion temperature and hence reduce the
formation of oxides of nitrogen.
[0003] It is known to mount an EGR valve on an engine manifold
where the valve is subjected to a harsh operating environment that
includes wide temperature extremes and vibrations. Stringent
demands are imposed by governmental regulation of exhaust emissions
that have created a need for improved control of such valves. Use
of an electric actuator is one means for obtaining improved
control, but in order to be commercially successful, such an
actuator must be able to operate properly in such extreme
environments for an extended period of usage. Moreover, in
mass-production automotive vehicle applications, component
cost-effectiveness and size may be significant considerations.
[0004] A known EGR valve typically relies on a valve that is
actuated by a movement of a valve stem by an electromagnetic
actuator. The EGR valve is typically mounted to a manifold or a
housing that has one port exposed to exhaust gases and another port
exposed to an intake manifold of the engine. Under certain
operating conditions, the valve abuts a valve seat surface so as to
prevent exhaust gases from flowing into the intake manifold.
Depending on the operating conditions, the valve can be moved away
from the seat to permit a controlled amount of exhaust gases into
the intake manifold.
[0005] An EGR valve having a linear actuator including a rotary
motor, which possesses more accurate, quicker and generally linear
responses can be advantageous by providing improved control of
tailpipe emissions, improved driveability, and/or improved fuel
economy for a vehicle having an internal combustion engine that is
equipped with an EGR system.
[0006] Further, an EGR valve having a linear actuator including a
rotary motor, which is more compact in size while delivering the
same or an increased magnitude of force over the travel of the
valve stroke can be advantageous because of limitations on
available space in a vehicle engine compartment. Thus, it would be
advantageous to provide for an EGR valve that is compact yet
powerful enough to deliver a generally constant force over an
extended stroke distance.
SUMMARY OF THE INVENTION
[0007] In one preferred embodiment, a method for assembling an
exhaust gas recirculation (EGR) valve is provided. This method
includes providing a base having a fluid conduit extending between
first and second ports, a valve member disposed within the fluid
conduit, and a valve shaft having a first end fixed to the valve
member and a second end, and mounting a linear actuator with a
rotary motor to the base, the actuator including a displaceable
member that is decoupled from the valve shaft.
[0008] In another embodiment, a method of operating an exhaust gas
recirculation valve is provided including the steps of providing a
valve portion including a valve member engaged with a valve seat
when the valve portion is in a closed position, a valve stem having
a longitudinal axis, a first end secured to the valve member and a
second end, and a spring that biases the valve member into
engagement with the valve seat. This method also includes the steps
of providing a linear actuator including a rotary motor and a
displaceable member coupled to the motor's rotor, wherein the
rotation axis of the rotor is substantially parallel to the
longitudinal axis, and opening the valve including pushing the
displaceable member into the valve stem second end.
[0009] In a method for closing an EGR valve, there includes the
steps of providing a linear actuator having a rotary motor,
providing a base, a valve member disposed within the base and being
engaged with a valve seat when the valve is closed and the valve
member being linear displaced from the valve seat when configured
from the closed to an open position, providing a spring disposed
below the actuator wherein the spring is compressed when the valve
is open and upon power loss to the motor, closing the valve
including expanding the compressed spring.
BRIEF DESCRIPTIONS OF THE DRAWINGS
[0010] The accompanying drawings, which are incorporated herein and
constitute part of this specification, illustrate embodiments of
the invention, and, together with the general description given
above and the detailed description given below, serve to explain
the features of the invention.
[0011] FIG. 1 is a cross-sectional view of an EGR valve configured
in an open position.
[0012] FIG. 2 is a cross-sectional view of the EGR valve of FIG. 1
configured in a closed position.
[0013] FIG. 3 illustrates a portion of an actuator of the EGR valve
of FIGS. 1 and 2 including a lead screw and a nut.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT(S)
[0014] FIGS. 1 and 2 illustrate cross-sectional views of an
embodiment of an exhaust gas recirculation EGR valve 10 according
to a preferred embodiment. EGR valve 10 includes a base 12, bracket
14 and a valve actuator 16. Actuator 16 includes any suitable
rotary motor (e.g., stepper, synchronous, DC) and a shaft 60
coupled to the motor's rotor. Preferably, a DC motor is used, and
more preferably, a brushless DC motor is used. Actuator 16 may be
used to configure valve 10 among a plurality of open positions and
a closed position on command from an engine control unit (ECU).
FIG. 2 illustrates a closed position and FIG. 1 illustrates one
such open position. Shaft 60 is linearly displaced by the motor for
purposes of applying a force to a valve stem 32 through surface
contact with stem 32. This applied force causes a valve member 34
to extend downward, disengaging valve member 34 from valve seat 36
and thereby configuring valve 10 in an open position (e.g., as
shown in FIG. 2). A compression spring 38 is preferably coupled to
stem 32 to bias valve member 34 into engagement with valve seat
36.
[0015] Valve seat 36 and valve member 34 are located within a fluid
conduit 18 formed by base 12. Base 12 provides a platform for
mounting valve stem 32, spring 38 and bracket 14 of valve 10, in
addition to its role in providing a fluid path for engine exhaust.
Specifically, base 12 forms a fluid conduit 18 extending between a
first port 20 and a second port 22. One of ports 20, 22 may be in
fluid communication with an engine intake or exhaust manifold. For
example, port 22 may face an intake manifold while port 20 faces a
return exhaust passageway from the engine.
[0016] A valve portion 30 of valve 10 includes stem 32, spring 38,
valve member 34 and valve seat 36. Stem 32, having a first and
second end 32a and 32b, respectively, is connected to valve member
34 at end 32b. End 32a is preferably formed with a curved surface
and includes a notched portion 32c for securing a cup 40 thereto.
Cup 40 preferably takes the shape of a frustoconical-like element
having a flange portion 40a. Valve seat 36 and valve member 34 are
made from a material suitably chosen to withstand high temperature
loading conditions associated with an EGR environment.
[0017] Valve member 34 and valve seat 36 form a pintle-type valve.
Other valve types may alternatively be used in place of a
pintle-type valve, e.g., a poppet valve. Valve member 34 is
upwardly tapered, and seat 36 is correspondingly shaped to receive
valve member 34 to establish a fluid-tight seal. When valve 10 is
configured in an open position, valve member 34 is disposed below
seat 36, as can be understand by comparing FIG. 1 with FIG. 2.
Valve stem 32 slides within a bearing element 44 that is retained
between a cup 42, gasket 14a, base 12 and a pin protector 47. At
one end bearing 44 abuts a stem seal 46 and at the other end cup
42. Seal 46, which is preferably made from a high temperature
graphite, is included in valve 10 to prevent exhaust gases from
leaking past valve stem 32.
[0018] In a preferred embodiment, a spring, and more preferably, a
linear spring 38 is used to bias valve member 34 into engagement
with seat 36. Spring 38 is retained between annular flange 40a and
flange 42a of cups 40 and 42, respectively. The distance between
flanges 42a and 40a, and/or a spring stiffness is chosen so that a
sufficient pre-load is applied to retain valve 10 in a closed
position using a pre-load in spring 38. Spring 38 is preferably a
compression spring. As valve 10 is configured from a closed
position to open position by applying a downward force on stem 32,
spring 38 is compressed between flanges 40a and 42a.
[0019] In the embodiment of valve 10 illustrated in FIGS. 1 and 2,
valve portion 30, which generally refers to spring 38, cups 40, 42,
stem 32 and valve member 34 may be decoupled from shaft 60 of
actuator 16. In other words, shaft 60 may be spaced from stem 32
(e.g., FIG. 2) so that only spring 38 influences the motion of
valve member 34. This decoupled end 32a is preferably formed with a
curved surface and when abutted with actuator 16, this curved
surface makes surface contact with a preferably flat face 61 of
shaft 60.
[0020] Decoupled shaft 60 and stem 32 allows for assembly without
having to maintain a precise alignment between two or more
components on an assembly line and will also tolerate slight
misalignments between the motor and shaft 60. A disc-shaped body
60c disposed at end 60a of shaft 60 can be included with shaft 60
so as to provide a relatively large contact area for stem 32 in the
event of slight misalignments during assembly. Decoupled shaft 60
also minimizes tolerance stack up problems from the valve 10
components.
[0021] Decoupled shaft 60 and stem 32 will also facilitate a
certain degree of tolerance for misalignments that may occur during
valve operations. For example, if the line of action of shaft 60
"shifts" over time such that the force applied to stem 32 by shaft
60 is no longer co-linear with the longitudinal axis of stem 32,
shaft 60 may still be capable of displacing valve member 34 from
seat 36 without imposing undue stress on actuator 16 bearings. A
misalignment, or "shift" between the line of action of shaft 60 and
the stem 32 longitudinal axis may result from, e.g., repeated
external mechanical vibrations that tend to loosen fittings between
valve 10 components. Bearing 44, which guides stem 32, may be sized
to allow a certain degree of "play" between stem 32 and bearing
44.
[0022] It is advantageous to minimize the amount of heat transfer
from regions of valve 10 in close proximity to exhaust gas to
actuator 16 because high actuator 16 temperatures can adversely
effect the performance of valve 10. Accordingly, a preferred
embodiment of an EGR valve, valve 10, includes an arrangement of
components that attempts to minimize the amount of heat that is
transferred from base 12 and/or stem 32 to actuator 16. Stem 32 and
shaft 60, when they make contact, do so over a relatively small
surface area. Additionally, bracket 14 is provided with openings or
cut-outs to allow air to come into contact with stem 32 and reduce
the amount of heat transfer to actuator 16. An insulating coramic
gasket 14a, for example, is disposed between bracket 14 and base
12, which also reduces the amount of heat transfer from base 12 to
bracket 14. Cups 40 and 42 may also be configured to dissipate heat
by forming flanges 40a, 42a as heat dissipating fins and cup 42 may
be used as a heat isolator from bearing 44.
[0023] As mentioned earlier, actuator 16 includes a rotary motor
and a mechanism that is capable of displacing shaft 60 towards or
away from stem 32. Specifically, actuator 16 includes a mechanism
that converts rotary motion of the motor's rotor to linear motion
in shaft 60. FIG. 3 illustrate a preferred embodiment of this
rotary to linear motion device. In this embodiment, shaft 60
includes a lead screw 62 having a threading 64 formed at end 60b
that is engaged with a threaded nut 66 that is coupled in rotation
to the motor's rotor. Lead screw 62 may include a pair of flanges
68 that are received in stationary slots or channels (not shown)
within actuator casing 16a to prevent rotation of shaft 60 relative
to nut 66. Thus, when a torque is applied to lead screw 62 through
nut 66, shaft 60 is linearly displaced as a result of the threaded
engagement with nut 66. Any suitable rotary motor having the
desired torque, speed and power characteristics may be used with
valve and its selection depends on the specific application.
[0024] In general, the factors that may be considered when
selecting the appropriate actuator for valve operations include:
ambient temperature (measured at the application site); self heat
rise of the motor (measured at application site with embedded
thermocouples); gross linear force (e.g., poppet valve
area.times.pressure+motor friction+pin friction.times.1.5);
diameter of the pintle; fail safe efficiency (e.g., (Torque.times.2
PI)/(axial force.times.lead screw length)=fail safe efficiency) and
return spring force (as discussed in greater detail below); and the
desired response to open and close the valve. Additionally, motor
parameters (e.g., as provided by a motor supplier) such as
resolution per revolution (a function of the number of poles);
detent torque; net force deference between gross and needed or
actual force; coefficient of friction of lead screw torque; and
coefficient of friction of shaft seal torque may be relevant to the
motor selection for a particular application.
[0025] Actuator 10 includes a failsafe capability, as alluded to
above. In one embodiment, valve 10 includes a failsafe return
spring, e.g., spring 38. In the event of a loss of power to the
motor, spring 38 is designed to effectively return the valve to the
closed position, which in the preferred embodiments requires that
the spring be capable of backdriving the actuator. In this regard,
the thread pitch should be suitably chosen so that it can be
backdriven by the spring. Any of a variety of actuators are
believed to include a thread pitch that can meet the requirements
for failsafe operations. Thus, the selection of a specific actuator
will generally vary from application to application. In selecting a
spring for a failsafe operation, the following calculation may be
performed to determine whether the valve will remain closed (i.e.,
whether the spring pre-load is acceptable) when the valve is
subjected to, e.g., a quasi-static 13 G load of the valve for the
following sample masses of component parts of a pintle-type valve
embodiment: TABLE-US-00001 (Mass of Pintle Assembly + 1/2 Spring
Mass + Mass of Upper Spring Cup)* Gload .ltoreq. Spring Preload ( (
21.45 .times. .times. grams + 0.5 .times. .times. ( 6 .times.
.times. grams ) + 7.56 .times. .times. grams ) * 1 .times. .times.
kg 1000 .times. .times. grams ) * .times. ( 13 .times. .times. G *
9.81 .times. .times. m .times. / .times. s 2 1 .times. .times. G )
.ltoreq. 25 .times. .times. N ##EQU1## 4.09 .times. kg .times.
.times. m s 2 = 4.09 .times. .times. N .ltoreq. 25 .times. .times.
N ##EQU2## *Typical EGR Gload of 13 G was used for this
calculation
[0026] In the illustrated embodiment, stem 32, valve member 34, cup
40, one half the mass of spring 38, and associated fasteners would
represent the mass in the above calculation.
[0027] While the present invention has been disclosed with
reference to certain embodiments, numerous modifications,
alterations and changes to the described embodiments are possible
without departing from the sphere and scope of the present
invention, as defined in the appended claims. Accordingly, it is
intended that the present invention not be limited to the described
embodiments, but that it has the full scope defined by the language
of the following claims, and equivalents thereof.
* * * * *