U.S. patent application number 09/841350 was filed with the patent office on 2001-08-23 for fluid flow valve with variable flow rate.
Invention is credited to Beverly, James A., Freigang, Alan R., Gerlofs, Kurt R..
Application Number | 20010015224 09/841350 |
Document ID | / |
Family ID | 22976319 |
Filed Date | 2001-08-23 |
United States Patent
Application |
20010015224 |
Kind Code |
A1 |
Freigang, Alan R. ; et
al. |
August 23, 2001 |
Fluid flow valve with variable flow rate
Abstract
An improved fluid flow valve (10) for a fluid flow control
system. The flow valve (10) includes a flow-regulating assembly
(40) having a housing (44) having a piston bore (15) within which
is slideably disposed a piston-like member (42). The piston-like
member (42) has a primary flow passage (52) and at least one
secondary flow passage (54) formed therein. A first portion (42a)
of the piston-like member (42) is configured for mating with a seat
(46) of the housing (44), and a resilient member (48) biases the
piston-like member (42) away from the seat (46). When at least a
predetermined fluid pressure differential exists, the first portion
(42a) mates with the seat (46) and causes the at least one
secondary flow passage (54) to be at least substantially closed
such that fluid can substantially flow only through the primary
flow passage (52).
Inventors: |
Freigang, Alan R.; (Scotts,
MI) ; Beverly, James A.; (Kalamazoo, MI) ;
Gerlofs, Kurt R.; (Kalamazoo, MI) |
Correspondence
Address: |
DYKEMA GOSSETT PLLC
39577 WOODWARD AVENUE
BLOOMFIELD HILLS
MI
48304-2820
US
|
Family ID: |
22976319 |
Appl. No.: |
09/841350 |
Filed: |
April 24, 2001 |
Related U.S. Patent Documents
|
|
|
|
|
|
Application
Number |
Filing Date |
Patent Number |
|
|
09841350 |
Apr 24, 2001 |
|
|
|
09257439 |
Feb 25, 1999 |
|
|
|
6250327 |
|
|
|
|
Current U.S.
Class: |
137/224 |
Current CPC
Class: |
G05D 7/0133 20130101;
Y10T 137/36 20150401; B60C 23/00372 20200501; Y10T 137/3631
20150401; Y10T 137/3646 20150401; B60C 23/00354 20200501; Y10T
137/778 20150401; B60C 23/00363 20200501; B60C 23/00318 20200501;
Y10T 137/7848 20150401 |
Class at
Publication: |
137/224 |
International
Class: |
F16K 015/20 |
Claims
We claim:
1. A wheel valve (10) assembly for adjusting the air pressure
within the pneumatic tires (62) of a vehicle comprising: a valve
housing (13) having a piston bore (15) formed therein; a piston
(42) having a plurality of axial flow passages (52, 54) formed
therein for axial translation within said piston bore (15); a valve
seat (46) formed in said housing (13) against which said piston
(42) contacts when in a closed position thereby causing a
predetermined number of said flow passages (54) to be sealed
against said valve seat (46) to reduce an effective total air flow
area of said flow passages (54), said piston (42) having an
increased total effective air flow area when said piston (42) is
not contacting said valve seat (46); a biasing means (48) acting to
urge said piston (42) away from said valve seat (46).
2. The wheel valve assembly (10) of claim 1, wherein said piston
(42) is moved to said closed position when an air pressure acting
against said piston (42) exceeds a predetermined level.
3. The wheel valve assembly (10) of claim 1, further comprising: an
inlet port (11) formed in said housing (13), said inlet port (11)
connected to an air source; an outlet port (20) formed in said
housing (13), said outlet port (20) connected to said pneumatic
tire (62).
4. The wheel valve assembly of claim 1, wherein said piston (42)
includes a first portion (42a) and a second portion (42b) where
said flow passages extend from said first portion (42a) to said
second portion (42b) and where said fluid pressure acts against
said first portion (42a) and said biasing means operates between
said second portion (42b) and said housing (13).
5. The wheel valve assembly of claim 1, wherein said biasing means
(48) is a coil spring acting between said housing (13) and said
piston (42).
6. The wheel valve assembly of claim 1, wherein said piston (42)
contacts said housing (13) at said valve seat (46) when in a closed
position and contacts one or more stops (49) when in a fully open
position.
7. The wheel valve assembly of claim 1, wherein said piston (42)
has a central axial flow passage (52) that remains continuously
open and one or more peripheral axial flow passages (54) that are
open except when said piston (42) is in said closed position.
8. A wheel valve assembly (10) for a vehicular tire air pressure
system (110), the assembly (10) comprising: a first housing (13)
including an inlet port (11) and an outlet port (20); a valve
device (22) in said first housing (13) including a valving member
(34) movable between open and closed positions for respectively
allowing and preventing air communication between said inlet (11)
and outlet (20) ports, a first resilient member (32) for biasing
said valving member (34) to said closed position, a valving surface
(26a) responsive to positive air pressure in said inlet port (11)
for moving said valving member (34) to said open position, and a
flow regulating assembly (40) comprising: a second housing (44)
having a first opening and a second opening and a piston bore (15)
formed therebetween, said second housing (44) including a seat
(46); a piston-like member (42) slideably disposed within said
piston bore (15) and having a primary flow passage (52) and at
least one secondary flow passage (54) formed therein for enabling
the flow of air between said openings of said second housing (44),
said piston-like member (42) having a first portion (42a) and a
second portion (42b), said first portion (42a) configured for
mating with said seat (46); a second resilient member (48) for
biasing said piston-like member (42) away from said seat (46); and
wherein said first portion (42a) mates with said seat (46) when at
least a predetermined air pressure differential exists between the
pressure at said second portion (42b) of said piston-like member
(42) and the pressure at said first portion (42a) of said
piston-like member (42), said mating causing said at least one
secondary flow passage (54) to be at least substantially closed
such that air can substantially flow only through said primary flow
passage (52).
9. The wheel valve assembly (10) as defined in claim 8 wherein said
valve device (22) is a single diaphragm valve device and said
valving member (34) and said valving surface (26a) comprise a
flexible diaphragm (26).
10. The wheel valve assembly (10) as defined in claim 8 wherein
said primary flow passage (52) and said at least one secondary flow
passage (54) are axially formed in parallel relationship within
said piston-like member (42).
11. The wheel valve assembly (10) as defined in claim 8 wherein
said at least one secondary flow passage (54) comprises two
secondary flow passages.
12. The wheel valve assembly (10) as defined in claim 11 wherein
the mating relationship of said first portion (42a) and said seat
(46) is frustoconical.
13. The wheel valve assembly (10) as defined in claim 8 wherein
said first resilient member (32) and said second resilient member
(48) each comprise a spring.
14. A flow-regulating assembly (40) for a fluid flow valve (10),
the assembly (40) comprising: a housing (44) having a first opening
and a second opening and a piston bore (15) formed therebetween,
said housing (44) including a seat (46); a piston-like member (42)
slideably disposed within said piston bore (15) and having a
primary flow passage (52) and at least one secondary flow passage
(54) formed therein for enabling the flow of fluid between said
openings of said housing (44), said piston10 like member (42)
having a first portion (42a) and a second portion (42b), said first
portion (42a) configured for mating with said seat (46); a
resilient member (48) for biasing said piston-like member (42) away
from said seat (46); and wherein said first portion (42a) mates
with said seat (46) when at least a predetermined fluid pressure
differential exists between the pressure at said second portion
(42b) of said piston-like member (42) and the pressure at said
first portion (42a) of said piston-like member (42), said mating
causing said at least one secondary flow passage (54) to be at
least substantially closed such that fluid can substantially flow
only through said primary flow passage (52).
15. The flow-regulating assembly (40) as defined in claim 14
wherein said primary flow passage (52) and said at least one
secondary flow passage (54) are axially formed in parallel
relationship within said piston-like member (42).
16. The flow-regulating assembly (40) as defined in claim 14
wherein said at least one secondary flow passage (54) comprises two
secondary flow passages.
17. The flow-regulating assembly (40) as defined in claim 16
wherein the mating relationship of said first portion (42a) and
said seat (46) is frustoconical.
18. The flow-regulating assembly (40) as defined in claim 14
wherein said resilient member (48) comprises a spring.
19. A method for regulating the flow of fluid through an internal
channel (38) of a fluid flow valve (10), the method comprising:
providing a primary flow passage (52) and a secondary flow passage
(54) within the channel (38); enabling the substantial flow of
fluid through both said primary flow passage (52) and said
secondary flow passage (54) when less than a predetermined fluid
pressure differential exists between the ends of the channel (38);
and substantially blocking said secondary flow passage (54) and
enabling a substantial flow of fluid through only said primary flow
passage (52) when at least said predetermined fluid pressure
differential exists between the ends of the channel (38).
20. A fluid flow valve assembly (10) comprising: a first housing
(13) including an inlet port (11) and an outlet port (20); a valve
device (22) in said first housing (13) including a valving member
(34) movable between open and closed positions for respectively
allowing and preventing air communication between said inlet (11)
and outlet (20) ports, and a flow regulating assembly (40)
comprising: a second housing (44) having a first opening and a
second opening and a piston bore (15) formed therebetween, said
second housing (44) including a seat (46); a piston-like member
(42) slideably disposed within said piston bore (15) and having a
primary flow passage (52) and at least one secondary flow passage
(54) formed therein for enabling the flow of fluid between said
openings of said second housing (44), said piston-like member (42)
having a first portion (42a) and a second portion (42b), said first
portion (42a) configured for mating with said seat (46); a
resilient member (48) for biasing said piston-like member (42) away
from said seat (46); and wherein said first portion (42a) mates
with said seat (46) when at least a predetermined fluid pressure
differential exists between the pressure at said second portion
(42b) of said piston-like member (42) and the pressure at said
first portion (42a) of said piston-like member (42), said mating
causing said at least one secondary flow passage (54) to be at
least substantially closed such that fluid can substantially flow
only through said primary flow passage (52).
21. The fluid valve assembly (10) as defined in claim 20 wherein
said valve device (22) is a single diaphragm valve device and said
valving member (34) and said valving surface (26a) comprise
diaphragm (26).
22. The fluid flow valve assembly (10) as defined in claim 20
wherein said primary flow passage (52) and said at least one
secondary flow passage (54) are axially formed in parallel
relationship within said piston-like member (42).
23. The fluid flow valve assembly (10) as defined in claim 20
wherein said at least one secondary flow passage (54) comprises two
secondary flow passages.
24. The fluid flow valve assembly (10) as defined in claim 23
wherein the mating relationship os said first portion (42a) and
said seat (46) is frusto-conical.
25. The fluid valve assembly (10) as defined in claim 20 wherein
said resilient member (48) comprises a spring.
Description
BACKGROUND OF THE INVENTION
[0001] The present invention relates to an improved valve for fluid
flow systems. In particular, the present invention is concerned
with an improved wheel valve for central tire inflation systems
(CTI systems), also known as onboard inflation systems and traction
systems, wherein the inflation pressure of vehicle tires may be
monitored and controlled from a remote location on the vehicle with
the vehicle at rest or in motion.
[0002] Various types of systems have been suggested in the past for
controllably inflating and deflating vehicle tires during vehicle
operation. Such systems typically include a source of air under
pressure and controls for selectively increasing or decreasing an
existing tire pressure, and for checking to determine the existing
tire pressure for each tire. The ability to selectively increase or
decrease tire pressure is desirable in connection with optimizing
the operation of the vehicle under widely changing conditions
including weather, vehicle load, terrain and vehicle speed. It is
also desirable to provide adaptability for isolating the air under
pressure in each vehicle tire from the remainder of the system so
that a problem such as a leak in one tire does not affect the air
pressure in the other tires. Further, in connection with such a
tire isolating feature, an air line from the system's source of air
under pressure extends to a vehicle tire generally through the
fixed axle upon which the tire and its associated wheel assembly
are rotatably mounted and across a sealing arrangement between the
fixed and rotating parts. The tire isolating wheel valve is
preferably between the sealing arrangement and tire so that the
sealing arrangement is not subjected to system air under pressure
other than at times of operation of the system to accomplish
inflation, deflation or pressure checking.
[0003] CTI systems are well known in the prior art, as may be seen
by reference to U.S. Pat. Nos. 5,253,687; 5,174,839; 5,273,064;
4,619,303; 4,754,792; 4,782,879; 4,825,925; 4,860,579; 4,877,048;
4,883,105; 4,893,664; 4,898,216; 4,917,163; 4,922,946; and
4,924,926. The entire disclosure of each of these patents is
incorporated herein by reference.
[0004] Generally, the prior art CTI systems have employed a
pneumatically controlled wheel valve that is affixed to each
vehicle wheel assembly for effecting tire pressure
inflation/deflation in response to pressure signals from an air
control circuit. The air control circuit is connected to each wheel
valve via a rotary seal assembly associated with each wheel valve.
Rotary seals are utilized which are located in a well protected
inboard location (see U.S. Pat. No. 4,434,833 assigned to the
Assignee of this invention), utilizing valves and conduits of a
relatively rugged proven construction which may be located at a
protected location or inside the vehicle tire to protect same.
Wheel valves automatically isolate those tires having less than a
predetermined minimum reference pressure from the remainder of the
system. Valve operations exhaust internal pressure on the rotary
seals during steady state operation of the system.
[0005] The above is accomplished by providing a central tire
inflation system for a vehicle utilizing a wheel valve assembly
comprising a wheel valve and a low tire pressure shutoff valve at
each wheel end assembly (usually a single or dual tire) where the
valve assembly is connected to the central control system by a
single pressure line or conduit through a rotary seal assembly and
pressurization of which single pressure conduit is effective to
open and close communication to the vehicle tire and to cause
inflation and/or deflation of said tire to a selected pressure. The
wheel valve assembly may be located exteriorly of the tire or may
be located interiorly of the tire such as in the bead lock portion
thereof. The low tire pressure shutoff valve is effective to
automatically isolate the tire associated therewith from the
remainder of the central tire inflation system when the inflation
pressure thereof is below a predetermined minimum reference value,
or when the system is in an inactive mode.
[0006] The single pressure conduit leading to the rotary seal at
the wheel hub assembly is connected to a source of pressurized
fluid through a plurality of control valves which are effective to
open communication to the tire to measure the existing pressurizing
thereof, to cause inflating or deflation of the tire as required,
to establish or block communication to the tire from the central
tire inflation system and to exhaust the single pressure line
during steady state conditions of the tire inflation system and to
relieve pressure on the rotary seals. Preferably, the control
valves, which may be separate or provided in a single valve block,
are operated by a control, preferably a microprocessor control,
which senses the tire inflation value selected by the operator,
senses vehicle velocity and the current pressure condition of the
tire pressures, vehicle air brake system and the inflation system
reservoir.
[0007] Although these prior art CTI systems have functioned well in
the past, newer applications for CTI systems have been developed
that have the dual requirements of fast deflation rates and the
capability of inflating the tires to high pressure levels (75 psig
and higher). Although some prior art systems are able to
accommodate both of these operating requirements, such systems are
undesirably complicated, typically requiring multi-diaphragm valves
and/or venting or exhausting at the wheel. Less complicated, single
diaphragm valve systems, without venting or exhausting at the
wheel, have heretofore been able to completely accommodate only one
of these two operating requirements. This is because prior art
single diaphragm valve systems have accommodated faster deflation
rates by using a wheel valve with a larger seat orifice through
which larger volumes of air can be exhausted. However, the widening
of the seat orifice causes increased pressure forces which tend to
keep the wheel valve open when high pressure shutoff is desired,
thus leading to degraded and less accurate shutoff performance and
a lowered maximum tire inflation pressure.
[0008] Since the rate of deflation varies exponentially with the
pressure differential between the tire and the ambient air, the
deflation rate slows considerably once lower tire pressures are
encountered. To maintain a relatively rapid rate of deflation at
these lower tire pressures, the opening of the exhaust valve must
be of a relatively large cross-sectional area to permit an outflow
of air.
[0009] A large cross-sectional area results in large forces when
the air pressure is at a high level because the force generated
when closing the valve is proportional to the cross-sectional area.
Specifically, the force is approximately equal to the air pressure
multiplied by the cross-sectional area. Thus, if an exhaust valve
having a large cross-sectional area is needed for rapid tire
deflation then large forces will be generated when closing off the
outlet at higher pressures. Using prior art valves, these forces
have exceeded the available closing force and the exhaust valve
remains open despite the command to close off. The challenge has
been how to obtain rapid deflation at low tire pressures while
limiting the pressure induced forces that must be handled in the
wheel valve at high pressure.
[0010] Another problem with prior art wheel valves is that they are
vented to atmosphere. The vent in the wheel valve provides an
opening through which contaminants such as dust and/or sand can be
drawn into the valve thereby causing operational failure of the
valve.
[0011] Thus, an improved single diaphragm wheel valve is needed
that, without exhausting or venting at the wheel, can accommodate
the newer CTI system applications by providing both fast deflation
rates and the capability of providing reliable valve shutoff at
high pressure levels.
SUMMARY OF THE INVENTION
[0012] The present invention provides an improved fluid flow valve
and associated flow-regulating assembly which meets all of the
above-identified needs for use as a wheel valve in a CTI
system.
[0013] The fluid flow valve of the present invention includes a
first housing having an inlet port and an outlet port. Within the
first housing is a valve device for allowing and preventing air
communication between the inlet and outlet ports. The valve device
includes a flow-regulating assembly having a second open-ended
housing within which is slideably disposed a piston-like member.
The piston-like member has a primary flow passage and at least one
secondary flow passage formed therein for enabling the flow of
fluid through the second housing. The piston-like member further
includes a first portion configured for mating with a seat of the
second housing, and a resilient member biases the piston-like
member away from the seat. When at least a predetermined higher
fluid pressure differential exists between the pressures at the
opposite sides of the piston-like member, the first portion mates
with the seat and causes the at least one secondary flow passage to
be at least substantially closed such that fluid can substantially
flow only through the primary flow passage.
[0014] One provision of the present invention is to provide an air
flow control valve having a relatively large orifice at lower
operating pressures.
[0015] Another provision of the present invention is to provide an
air flow control valve having a relatively large orifice which can
be reliably closed at any operating pressure.
[0016] Another provision of the present invention is to provide an
airflow control valve for a central tire inflation system which
accommodates downstream flow restrictions.
[0017] Another provision of the present invention is to provide an
air flow control valve having a relatively large orifice for
operation at lower operating pressures and a relatively small
orifice for operation at higher operating pressures.
[0018] Another provision of the present invention is to provide an
air flow control valve for a central tire inflation system having a
relatively large orifice for operation at low tire pressures and a
smaller orifice for operation at higher tire pressures.
[0019] Still another provision of the present invention is to
provide an air flow control valve for a central tire inflation
system having a relatively large orifice for operation at low tire
pressures and a smaller orifice for operation at higher tire
pressures with no external venting.
[0020] Other details, objects, and advantages of the present
invention will become more apparent with a reading of the following
description.
BRIEF DESCRIPTION OF THE DRAWINGS
[0021] FIG. 1 is an enlarged sectional view of a wheel valve
assembly embodying the present invention.
[0022] FIG. 2 is an enlarged view of the piston or flow-regulating
assembly of the wheel valve assembly of FIG. 1, shown in normal
position.
[0023] FIG. 3 is a view of the piston assembly of FIG. 2, shown in
a closed, flow restricted, position.
[0024] FIG. 4 is a cross-sectional view of a part of the piston
assembly of FIG. 3, taken along the line IV-IV.
[0025] FIG. 5 is a schematic illustration of an example vehicular
central tire inflation system in which the present invention may be
implemented.
DESCRIPTION OF THE PREFERRED EMBODIMENT
[0026] In the following description of the present invention,
certain terms will be utilized for purposes of reference only and
are not intended to be limiting. The terms "upward", "downward",
"rightward" and "leftward" refer to directions in the drawings to
which reference is made. The terms "inward" and "outward",
respectively, refer to directions towards and away from,
respectively, the geometric center of the device described. The
terms "inflation" and "deflation, respectively, refer to increased
and decreased, respectively, pressurization of a tire or the like.
Said terminology will include the words above specifically
mentioned, derivatives thereof and words of similar import.
[0027] Referring now to FIG. 1, shown is an enlarged sectional view
of wheel valve assembly 10 embodying the present invention.
Assembly 10 comprises a valve housing 13 including a housing body
12 having a piston bore 15 formed therein and a housing cover 14, a
control port 16 in continuous communication with inlet port 11
(that is connected to conduit 100 through an annular chamber 82 at
the axle housing 86, see FIG. 5), a channel 18, tire or outlet port
20, and a valve device 22 operative to both allow and prevent air
communication between control port 16 and tire port 20. In the
preferred embodiment, valve device 22 is a diaphragm valve device,
as described below. Housing body 12 and housing cover 14 are
secured together by a plurality of fasteners 24.
[0028] Diaphragm valve device 22 includes a spring chamber 28, a
flexible diaphragm 26 that separates spring chamber 28 from control
port 16, a rigid cup-shaped member 30 slideably disposed in spring
chamber 28 and biased against diaphragm 26 by a spring 32, a
valving member 34 defined by a center portion of diaphragm 26, and
a valve seat 36 disposed at one end of a passage 38 that
communicates at its other end with tire port 20 via a channel 18.
Spring 32 biases valving member 34 into a closed position or
sealing engagement with valve seat 36 with a force sufficient to
maintain the sealing engagement when the highest contemplated tire
pressure is experienced.
[0029] Valving member 34 is moved to an open position against the
force of spring 32 in response to a predetermined minimum positive
air pressure in control port 16 acting on diaphragm surface 26a.
Such an air pressure may be provided by any suitable air control
circuit known to one of ordinary skill in the art. In this manner,
inflation or deflation of a vehicle's tire may be effected. If the
air pressure acting on diaphragm surface 26a is greater than the
tire pressure of tire port 20 (and at least the predetermined
minimum positive air pressure to open valving member 34), then air
will flow into the tire, thus causing inflation. If the air
pressure acting on diaphragm surface 26a is less than the tire
pressure of tire port 20 (but at least the predetermined minimum
positive air pressure to open valving member 34), then air will
flow out of the tire, thus causing deflation.
[0030] Diaphragm valve device 22 also includes a piston or
flow-regulating assembly 40 disposed within passage 38. As shown in
greater detail in FIGS. 2 and 3, piston assembly 40 of a preferred
embodiment comprises a piston 42 slideably disposed within the
piston bore 15 of an open-ended housing 44 and biased away from a
seat 46 by a resilient member preferably comprising a spring 48.
Stops 49 are included in housing 44 in order to limit the range of
movement of piston 42. As described in greater detail below, the
amount of compression of spring 48, and therefore the position of
piston 42, depends upon the pressure differential between the top
or first portion 42a and bottom or second portion 42b of piston 42.
Piston 42 has internal channels or passages axially formed therein
comprising a primary or main flow passage 52 and secondary flow
passages 54. Fluid may flow in either direction through these flow
passages, as described in greater detail below. FIG. 4 shows a
cross-sectional view of piston-like member 42 taken along the line
IV-IV of FIG. 3, showing the shape and configuration of the
parallel flow passages 52 and 54 of the preferred, non-limiting
embodiment.
[0031] FIG. 2 shows piston assembly 40 in the "increased flow"
position, with spring 48 in its fully expanded state and both
primary and secondary flow passages 52 and 54 open. Piston assembly
40 is moved to a fully open position where the piston 42 contacts
the stops 49. When the tire is being filled with air the fluid is
flowing in a downward direction thereby filling the tire, the
piston 42 is moved toward the stops 49 by action of the spring 48
and both the flow passages 54 and the primary flow passage 52. FIG.
3 shows piston assembly 40 in the closed or "reduced flow"
position, with spring 48 in its fully compressed state and
secondary flow passages 54 substantially closed.
[0032] The top portion 42a of piston 42 is suitably configured to
mate with piston seat 46 when piston 42 is at the top of its
potential travel path. In the preferred, non-limiting embodiment
shown in FIGS. 1-3, the mating relationship of top portion 42a and
seat 46 is frusto-conical. This mating causes secondary flow
passages 54 to become at least substantially closed, thus enabling
fluid to substantially flow only through primary flow passage 52
when fluid is flowing in an upward direction thereby lowering the
tire pressure in a CTI system. Spring 48 becomes substantially
compressed and enables such mating between portion 42a and piston
seat 46 whenever the pressure at or near bottom portion 42b of
piston 42 exceeds the pressure at or near top portion 42a of piston
42 by at least a predetermined amount--in other words, whenever at
least a predetermined fluid pressure differential exists.
[0033] The value of the above-mentioned predetermined fluid
pressure differential for a particular flow-regulating assembly 40
depends upon many factors, including without limitation the surface
areas and configurations of top and bottom portions 42a and 42b of
piston 42, the dimensions of primary and secondary flow passages 52
and 54, and the resiliency of resilient member 48. Those
characteristics shown in FIGS. 1-3 are only of a preferred
embodiment of piston assembly 40. By adjustment of these factors,
one may establish an appropriate value for the predetermined fluid
pressure differential for a given situation, thereby ensuring that
the reduced flow position is assumed at the desired time for
appropriate shutoff performance.
[0034] The appropriate dimensions of primary and secondary flow
passages 52 and 54 depends upon the application. In the vehicular
tire pressure system environment, in which the operation of the
invention is described in detail below, primary flow passage 52
should be small enough so that, at the highest contemplated tire
pressure levels, the volume of fluid flowing therethrough does not
exert undesirably large back pressures on valving member 34 when
piston assembly 40 is in the reduced flow position. What
constitutes excessive back pressure depends upon the composition
and surface area of valving member 34 of diaphragm 26 and upon
other sources of flow restriction such as rotary seals 78 and 80
(see FIG. 5). Secondary flow passages 54 should be dimensioned so
that, when piston assembly 40 is in the normal increased flow
position (see FIG. 2), the flow rate through passages 54 in
combination with the flow rate through primary flow passage 52
enables fast deflation at a desired rate when medium to low tire
pressures exist.
[0035] Piston 42 preferably, but not necessarily, includes an
O-ring 50, preferably of conventional polymer material, that
provides a sealing engagement between piston 42 and the sides of
piston housing 44 whereby any flow of fluid through valve device 22
is only through flow passage 52 and (possibly) flow passages
54.
[0036] In operation of wheel valve assembly 10 in a vehicular tire
pressure system, piston assembly 40 is in the increased flow
position (such as that shown in FIG. 2) throughout an inflation
sequence due to the force generated by the spring 48. Upon
termination of an inflation sequence when shutoff takes place, the
air pressure acting on diaphragm surface 26a becomes lower than the
predetermined minimum positive air pressure required to keep
valving member 34 open. In this shutoff situation, the position of
piston assembly 40 depends upon the pressure to which the tire has
been inflated. If the differential pressure due to the air flow
through the valve 10 is high enough, then the pressure at bottom
portion 42b of piston 42 will exceed the pressure at top portion
42a by at least the predetermined amount. This causes piston
assembly 40 to assume the reduced flow position shown in FIG. 3. In
the reduced flow position, fluid can substantially flow outward
(from tire port 20 to the inlet port) only through primary flow
passage 52, thus reducing the back pressure exerted on valving
member 34 by the relatively high tire pressure. This enables
valving member 34 to close leading to improved shutoff performance
whereby increased specific maximum tire inflation pressures can be
accurately attained. It should be noted that the closing of valving
member 34 will cause the pressures on both sides of piston 42 to
eventually equalize, thereby causing piston assembly 40 to
eventually assume the increased flow position such as that shown in
FIG. 2 due to force generated by spring 48.
[0037] If, on the other hand, the tire pressure at tire port 20 is
not high enough at inflation shutoff to cause the pressure at
bottom portion 42b of piston 42 to exceed the pressure at top
portion 42a by at least the predetermined amount, then piston
assembly 40 will remain in the increased flow position such as that
shown in FIG. 2. Although fluid can flow through all flow passages
in this situation, the back pressure exerted on valving member 34
is relatively low due to the lower tire pressure. This enables
valving member 34 to still close resulting in good shutoff
performance and the ability to accurately inflate to particular
tire pressures.
[0038] In a deflation sequence, the air pressure acting on
diaphragm surface 26a is less than the tire pressure of tire port
20. Thus, the pressure at bottom portion 42b of piston 42 is
greater than the pressure at top portion 42a. The position of
piston assembly 40 depends upon whether or not this fluid pressure
differential is at least equal to the predetermined fluid pressure
differential described above. At the beginning of the typical
deflation sequence when high tire pressures exist, the fluid
pressure differential is greater than the predetermined fluid
pressure differential, thus causing piston assembly 40 to be in the
reduced flow position of FIG. 3. This position, although less
conducive to deflation since flow is hampered, does not seriously
affect deflation times because the large pressure differential
forces air quickly out through primary flow passage 52. It should
be noted that the reduction in outward flow caused by movement into
the reduced flow position causes the pressure differential to
increase beyond the predetermined fluid pressure differential,
thereby at least temporarily "latching" piston assembly 40 in that
position. However, if the deflation sequence continues, eventually
the fluid pressure differential will be less than the predetermined
differential, thus causing piston assembly 40 to assume the
increased flow position such as that shown in FIG. 2. In this
situation, the smaller pressure differential is unable to force air
out with as much force as before since the rate of flow decreases
exponentially with pressure. However, the additional flow area
through secondary flow passages 54 compensates for this smaller
pressure differential and enables deflation to continue at an
increased rate.
[0039] Upon termination of a deflation sequence when shutoff takes
place, the air pressure acting on diaphragm surface 26a becomes
lower than the predetermined minimum positive air pressure required
to keep valving member 34 open. Similar to the inflation shutoff
situation, the position of piston assembly 40 in the deflation
shutoff situation depends upon the pressure to which the tire has
been deflated. If the tire pressure at tire port 20 is high enough,
then the pressure at bottom portion 42b of piston 42 will exceed
the pressure at top portion 42a by at least the predetermined
amount. This causes piston assembly 40 to be in the reduced flow
position shown in FIG. 3. In the reduced flow position, fluid can
substantially flow outward only through primary flow passage 52,
thus reducing the back pressure exerted on valving member 34 by the
relatively high tire pressure. This enables valving member 34 to
close leading to improved shutoff performance and the ability to
accurately deflate to particular tire pressures.
[0040] If, on the other hand, the tire pressure at tire port 20 is
not high enough at deflation shutoff to cause the pressure at
bottom portion 42b of piston 42 to exceed the pressure at top
portion 42a by at least the predetermined amount, then piston
assembly 40 will be in the increased flow position such as that
shown in FIG. 2. Although fluid can flow through all flow passages
in this situation, the back pressure exerted on valving member 34
is relatively low due to the lower tire pressure. This enables
valving member 34 to still close again resulting in good shutoff
performance and the ability to accurately deflate to particular
tire pressures.
[0041] Although the preferred embodiment of the present invention
is shown with two secondary flow passages 54 formed in piston-like
member 42, it should be understood that one such secondary flow
passage, or three or more secondary flow passages, may be employed.
Also, flow passages 52 and 54 can be of any suitable shape or form,
and piston seat 46 and top portion 42a of piston 42 can be
configured in any mating relationship whereby at least one
secondary flow passage is substantially closed when piston 42 is at
the top of its potential travel path. Furthermore, although spring
48-is implemented in the preferred embodiment, it should be
recognized that any suitable resilient member may be employed in
place thereof.
[0042] Although piston or flow-regulating assembly 40 is
implemented in the preferred embodiment in a single diaphragm
valve, it should be appreciated that flow-regulating assembly 40
can be implemented in a multi-diaphragm valve, or any other type of
fluid flow valve, as well.
[0043] The variable flow valve and associated flow-regulating
assembly of the present invention finds application in any type of
fluid flow control system, where fluid may comprise any matter of
substantially gaseous or liquid form. The present invention is
described below with particular reference to wheel valves of
vehicular tire air pressure systems, specifically single-diaphragm
wheel valves, for exemplary purposes only. Because the general
structure and functioning of such tire pressure systems are well
known in the art, the components of such systems, apart from the
wheel valves, are not described in great detail herein except as
follows.
[0044] The pneumatic components of the central tire inflation
system 60 as utilized to control the inflation pressure of a single
tire 62 may be seen by reference to FIG. 5. Inflatable tire 62 is
mounted to a tire rim 64 which is fixed to a wheel hub assembly 66
rotationally supported on the outer end of an axle housing 68 by
means of bearings 70. An axle shaft (not shown) rotationally driven
by conventional means, such as a differential (not shown), extends
from the axle housing 68 and typically includes a flange (not
shown) for drivingly connecting the axle shaft to the wheel hub. As
may be seen in greater detail by reference to U.S. Pat. No.
4,434,833, assigned to the Assignee of this invention, an annular
sleeve 74 may be pressed to the axle housing at a location inboard
of the bearings 70 and the wheel hub may define and inboardly
extending sleeve-type annular flange 76 telescopically surrounding
sleeve 74. A pair of rotary seals 78 and 80 extend radially between
the outer periphery of sleeve 74 and the inner periphery of
sleeve-type flange 76 to define an annular sealed chamber 82
therebetween. Sleeve 74 is provided with an inlet 84 and a passage
86 opening to the chamber 82. Sleeve-type flange 76 is provided
with a 30 generally radially extending passage 88 extending from
the sealed annular chamber 82 to the exterior outer diameter
surface thereof. A single passage 90 may be provided in the radial
flange portion 92 of the wheel hub 66 for passage of a pressure
conduit. The above construction is described in above mentioned
U.S. Pat. No. 4,434,833 and forms no part of the present invention.
It is understood, of course, that the present invention is equally
applicable to wheel hub/axle housing assemblies (also called
"wheel-end assemblies") of other constructions.
[0045] The central tire inflation system 60 may be considered to
comprise two components, a stationary components 96 fixed to the
vehicle chassis and a rotational component 98 rotationally fixed to
the wheel hub 66 and tire 62. The stationary component 96 is
fluidly connected to the rotational component 98 by means of the
annual chamber 82 defined by the rotary seals 78 and 80. Briefly,
fluid conduit 100 from the stationary component 96 is fluidly
connected to the inlet 84 of passage 86 formed in sleeve 74 while
fluid conduit 102 leading to the rotational component 98 is fluidly
connected to the passage 88 formed in sleeve-type flange 76 and
passes through the opening 90 defined in the flange 92 of the hub
66. To protect conduit 102, a grommet or bushing 104 may be
provided in the opening 90 or opening 90 may be defined by a bore
in a wheel stud. Of course, alternatively, a passage may be
provided in hub 66 opening to the outboard side thereof. It may
thus be seen that attachment of system 60 to a wheel end assembly
requires no drilling of the axle housing 68 and drilling of only a
single hole 90 through radial flange 92 of the wheel hub 66. It is
noted that the rotary seals 78 and 80 and the conduit 100 leading
to the wheel end assembly may be located inboard of the bearings 70
in a relatively protected location on the vehicle.
[0046] Rotating component 98 of system 60 includes a low pressure
shutoff valve 106, a control valve 108 which can be combined into
one wheel valve assembly 10 as shown in FIG. 1 and is the subject
of the present invention, and a manual inflate and pressure check
valve 60. The wheel valve assembly 10 (low pressure valve 106 and
control valve 108) may be located interiorly of tire 62.
[0047] A manifold portion 112 of conduit 102 interconnects ports
114 and 116 of valves 106 and 108, respectively, with one another
and with the conduit 100 via chamber 82 while a manifold conduit
118 interconnects ports 120 and 122 of valves 106 and 108,
respectively, the manual inflate and check valve 110, and with the
interior chamber 124 of the inflatable pneumatic tire 62. The
present invention combines the shutoff valve 106 with the control
valve 108 into a wheel valve assembly 10 having an inlet port 111
and an outlet port 123. A conduit 126 interconnects ports 128 and
130 of valves 106 and 108, respectively. If dual tires are
utilized, manifold conduit 118 may be split downstream of the valve
110 and manual shutoff valves provided to isolate the tires if
required.
[0048] The relatively stationary portion 96 of the central tire
inflation system 60 is mounted at convenient points on the vehicle
chassis, preferably above the fording level of the vehicle, and is
fluidly connected to the rotating portion 98 by means of a single
conduit 100 and a single rotating seal chamber 82.
[0049] The relatively stationary portion 96 includes a source of
pressurized fluid 142 which is typically the vehicle air system
compressor, or, preferably, a pressurized air reservoir supplied by
the compressor. Heavy duty trucks are typically equipped with an
air compressor for an onboard compressed air system consisting of
air brakes, transmission and/or axle shift actuators and/or
controls, air suspensions and the like. If the vehicle is not
otherwise provided with an air system, a separate compressor and/or
reservoir or may be provided for the central tire inflation system
60.
[0050] The source of pressurized fluid supplies compressed air to a
split conduit 144 which defines branches 146 and 148 leading to the
inlets 150 and 152, respectively, of inflate valve 154 and pressure
regulator 156, respectively. Pressure regulator 156 defines an
outlet 158 connected to a conduit 160 leading to the outlet 162 of
deflate valve 164. The outlet 166 of inflate valve 154 and inlet
168 and deflate valve 164, respectively, are connected to a
manifold conduit 170. Manifold conduit 170 is also connected to the
inlet 172 of shutoff valve 174. Shutoff valve 174 has an outlet 176
connected to exhaust. Manifold conduit 170 is also connected to
port 178 of quick-release valve 180. A pressure transducer 186 is
exposed to the pressure in conduit 170 by means of a branch conduit
188.
[0051] Quick-release valve 180 defines a port 182 connected to
exhaust and a port 184 connected to the conduit 100 leading to the
wheel end assembly.
[0052] Pressure regulator 156 may be of any conventional design and
will limit pressure flowing therethrough to conduit 160 to a
relatively low pressure of about 8-18 psi, and further includes a
relief port 190 leading to exhaust. Accordingly, it may be seen
that the inlet 150 to the inflation valve 154 is exposed to supply
pressure while the outlet 162 of deflate valve 164 is in
communication with a regulated pressure of about 8-10 psi. As will
be seen, pressure regulator 156 regulates the quick-release valve
180 and thus regulates the minimum pressure to which system 60 will
deflate tire 62.
[0053] Inflate valve 154, deflate valve 164 and shutoff valve 174
are each relatively small flow two-way valves, preferably solenoid
controlled valves, of conventional design. Valves 154, 164 and 174
have a first or closed position blocking fluid flow between the
inlet and outlet ports thereof and a second or open position
permitting fluid flow between the inlet and outlet ports thereof.
Typically, the solenoid two-way valves 154 and 164 are spring
biased to the closed positions thereof while valve 174 is spring
biased to the open position thereof.
[0054] As described above, the present invention provides an
improved flow valve and associated flow-regulating assembly. In
particular, the present invention provides an improved single
diaphragm wheel valve that accommodates fast deflation rates and
the capability of inflating tires to high pressure levels.
[0055] While the present invention has been described with a
certain degree of particularity, it is understood that certain
modifications of the invention and substitution and rearrangement
of the parts therein may be possible and may be apparent to those
skilled in the art from a reading and understanding of the
specification. It is intended that all such modifications,
substitutions, and rearrangements are included in the invention,
insofar as they come within the spirit and scope of the appended
claims.
* * * * *