U.S. patent application number 09/819585 was filed with the patent office on 2002-01-03 for robust hydrodynamic brush seal.
Invention is credited to Justak, John F..
Application Number | 20020000694 09/819585 |
Document ID | / |
Family ID | 26890837 |
Filed Date | 2002-01-03 |
United States Patent
Application |
20020000694 |
Kind Code |
A1 |
Justak, John F. |
January 3, 2002 |
Robust hydrodynamic brush seal
Abstract
A brush seal for sealing a circumferential gap between two
relatively rotating machine components, e.g. the rotor or shaft and
stator of a fluid flow machine, such as a gas turbine engine. One
end of a plurality of seal bristles is fixed in an annular shape
and are mounted to the stator, and their opposite ends are attached
to a number of individual shoes located at the rotor. The shoes
function very similarly to that of a tilting pad bearing shoe.
Prior to shaft rotation, the shoes are in contact with the rotor
surface with preferably the leading edge of each shoe set to have
less contact than the trailing edge of the shoe. As such, when the
rotor begins to rotate, a hydrodynamic wedge is created which lifts
the shoe slightly off the surface of the shaft allowing the shoe to
effectively "float" over the shaft at a design gap.
Inventors: |
Justak, John F.; (Stuart,
FL) |
Correspondence
Address: |
HOLLAND & KNIGHT, LLP
ONE EAST BROWARD BLVD.
SUITE 1300
FT LAUDERDALE
FL
33301
|
Family ID: |
26890837 |
Appl. No.: |
09/819585 |
Filed: |
March 28, 2001 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
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60195249 |
Apr 3, 2000 |
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Current U.S.
Class: |
277/355 |
Current CPC
Class: |
F16J 15/442 20130101;
F16J 15/3288 20130101 |
Class at
Publication: |
277/355 |
International
Class: |
F16J 015/44 |
Claims
What is claimed is:
1. A brush seal for sealing a circumferential gap between a first
machine component and a second machine component which is rotatable
relative to the first machine component, comprising: a number of
seal bristles each having a first end and a second end, said first
ends of said seal bristles being mounted to said first machine
component and said second ends extending in a direction toward said
second machine component; at least one shoe extending about the
second machine component, said at least one shoe being mounted to
said second ends of said seal bristles in at least one location
therealong so that said seal bristles are prevented from directly
contacting the second machine component.
2. The brush seal of claim 1 in which said at least one shoe
comprises a number of individual shoes oriented end-to-end about
the second machine component.
3. The brush seal of claim 2 in which each of said shoes is mounted
at two discrete locations to said second ends of said seal
bristles.
4. The brush seal of claim 3 in which said shoes are mounted to
said second ends of said brush seals by welding.
5. The brush seal of claim 2 in which each of said shoes has a
leading edge and a trailing edge, each of said shoes being mounted
to said second ends of said brush seals so that said leading edge
thereof is located further away from said second machine component
than said trailing edge.
6. The brush seal of claim 1 further including a low pressure
backing plate and a spaced, high pressure backing plate, said seal
bristles extending within said space between said low pressure
backing plate and said high pressure backing plate.
7. A brush seal for sealing a circumferential gap between a first
machine component and a second machine component which is rotatable
relative to the first machine component, comprising: a number of
seal bristles each having a first end and a second end, said first
ends of said seal bristles being mounted to said first machine
component and said second ends extending in a direction toward said
second machine component; a number of individual shoes oriented
end-to-end about the second machine component with a space between
adjacent shoes, each of said shoes having a leading edge and a
trailing edge, each of said shoes being affixed at spaced locations
to said second ends of said seal bristles so that said leading edge
thereof is positioned further away from the second machine
component than said trailing edge, said seal bristles being
prevented by said shoes from directly contacting the second machine
component.
8. A brush seal for sealing a circumferential gap between a first
machine component and a second machine component which is rotatable
relative to the first machine component, comprising: a number of
seal bristles each having a first end and a second end, said first
ends of said seal bristles being mounted to said first machine
component and said second ends extending in a direction toward said
second machine component. a low pressure backing plate spaced from
a high pressure backing plate, said seal bristles extending within
said space between said low pressure and high pressure backing
plates, an orifice being formed between said low pressure backing
plate and said seal bristles which is connected to a port formed in
said high pressure backing plate; at least one shoe extending about
the second machine component, said at least one shoe being mounted
to said second ends of said seal bristles in at least one location
therealong so that said seal bristles are prevented from directly
contacting the second machine component.
9. The brush seal of claim 8 in which said port is effective to
transmit high pressure fluid into said orifice, said fluid within
said orifice substantially reducing contact between said brush
seals and said low pressure backing plate.
10. The brush seal of claim 8 in which said orifice is formed by a
ring mounted at one end of said low pressure backing plate which
extends toward said bristle seals, and an extension protruding from
said at least one shoe into contact with the other end of said low
pressure backing plate.
11. The brush seal of claim 8 in which said at least one shoe
comprises a number of individual shoes oriented end-to-end about
the second machine component.
12. The brush seal of claim 11 in which each of said shoes is
mounted at two discrete locations to said second ends of said seal
bristles.
13. The brush seal of claim 12 in which said shoes are mounted to
said second ends of said brush seals by welding.
14. The brush seal of claim 11 in which each of said shoes has a
leading edge and a trailing edge, each of said shoes being mounted
to said second ends of said brush seals so that said leading edge
thereof is located further away from said second machine component
than said trailing edge.
Description
[0001] This application claims priority under 35 U.S.C. .sctn.
119(e) to U.S. Provisional Application Ser. No. 60/195,249 for all
commonly disclosed subject matter. U.S. Provisional Application
Ser. No. 60/195,249 is expressly incorporated herein by reference
in its entirety to form a part of the present disclosure.
[0002] Field of the Invention
[0003] This invention relates to seals for sealing a
circumferential gap between two machine components that are
relatively rotatable with respect to each other, and, more
particularly, to a hybrid brush seal having a plurality of bristles
that are mounted in a ring shape on a first machine component and
that have bristle ends directed at sealing surface of the second,
rotating machine component, whereby the bristle ends are titled at
an angle in the circumferential direction in the annular plane of
the bristles, primarily in the direction of shaft rotation. The
bristle ends are kept from direct contact with the rotating machine
component via one or more shoes which are designed such that as the
shaft rotates a hydrodynamic film will separate the shoe from the
shaft. The shoe(s) is attached to the bristle ends at discreet
locations.
BACKGROUND OF THE INVENTION
[0004] Turbomachinery, such as gas turbine engines employed in
aircraft, currently is dependent on either labyrinth (see FIGS.
1A-1E), brush (see FIGS. 2A and 2B) or carbon seals for critical
applications. Labyrinth seals provide adequate sealing, however,
they are extremely dependent on maintaining radial tolerances at
all points of engine operation. The radial clearance must take into
account factors such as thermal expansion, shaft motion, tolerance
stack-ups, rub tolerance, etc. Minimization of seal clearance is
necessary to achieve maximum labyrinth seal effectiveness. In
addition to increased leakage if clearances are not maintained,
such as during a high-G maneuver, there is the potential for
increases in engine vibration. Straight-thru labyrinth seals (FIG.
1A) are the most sensitive to clearance changes, with large
clearances resulting in a carryover effect. Stepped labyrinth seals
(FIGS. 1B and 1C) are very dependent on axial clearances, as well
as radial clearances, which limits the number of teeth possible on
each land. Pregrooved labyrinth seals (FIG. 1D) are dependent on
both axial and radial clearances and must have an axial clearance
less than twice the radial clearance to provide better leakage
performance than stepped seals.
[0005] Other problems associated with labyrinth seals arise from
heat generation due to knife edge to seal land rub, debris from
hardcoated knife edges or seal lands beings carried through engine
passages, and excessive engine vibration. When seal teeth rub
against seal lands, it is possible to generate large amounts of
heat. This heat may result in reduced material strength and may
even cause destruction of the seal if heat conducted to the rotor
causes further interference. It is possible to reduce heat
generation using abradable seal lands, however, they must not be
used in situations where rub debris will be carried by leakage air
directly into critical areas such as bearing compartments or carbon
seal rubbing contacts. This also holds true for hardcoats applied
to knife edges to increase rub capability. Other difficulties with
hardcoated knife edges include low cycle fatigue life debits, rub
induced tooth-edge cracking, and the possibility of handling
damage. Engine vibration is another factor to be considered when
implementing labyrinth seals. As mentioned previously, this
vibration can be caused by improper maintenance of radial
clearances. However, it can also be affected by the spacing of
labyrinth seal teeth, which can produce harmonics and result in
high vibratory stresses.
[0006] In comparison to labyrinth seals, brush seals can offer very
low leakage rates. For example, flow past a single stage brush seal
is approximately equal to a four knife edge labyrinth seal at the
same clearance. Brush seals are also not as dependent on radial
clearances as labyrinth seals. Leakage equivalent to approximately
a 2 to 3 mil gap is relatively constant over a large range of
wire-rotor interferences. However, with current technology, all
brush seals will eventually wear to line on line contact at the
point of greatest initial interference. Great care must be taken to
insure that the brush seal backing plate does not contact the rotor
under any circumstances. It is possible for severing of the rotor
to occur from this type of contact. In addition, undue wire wear
may result in flow increases up to 800% and factors such as changes
in extreme interference, temperature and pressure loads, and
rubbing speeds must be taken into account when determining seal
life.
[0007] The design for common brush seals, as seen in FIGS. 2A and
2B, is usually an assembly of densely packed flexible wires
sandwiched between two plates. The free ends of the wires protrude
beyond the plates and contact a land or runner, with a small radial
interference to form the seal. The wires are angled so that the
free ends point in the same direction as the movement of the
runner. Brush seals are sized to maintain a tight diametral fit
throughout their useful life and to accommodate the greatest
combination of axial movement of the brush relative to the
rotor.
[0008] Brush seals may be used in a wide variety of applications.
Although brush seal leakage generally decreases with exposure to
repeated pressure loading, incorporating brush seals where extreme
pressure loading occurs may cause a "blow over" condition resulting
in permanent deformation of the seal wires. Brush seals have been
used in sealing bearing compartments, however coke on the wires may
result in accelerated wear and their leakage rate is higher than
that of carbon seals.
[0009] One additional limitation of brush seals is that they are
essentially uni-directional in operation, i.e., due to the
angulation of the individual wires, such seals must be oriented in
the direction of rotation of the moving element as depicted by the
arrow in FIG. 2A. Rotation of the moving element or rotor in the
opposite direction, against the angulation of the wires, can result
in permanent damage and/or failure of the seal. In the particular
application of the seals required in the engine of a V-22 Osprey
aircraft, for example, it is noted that during the blade fold wing
stow operation, the engine rotates in reverse at very low rpm's.
This is required to align rotor blades when stowing wings. This
procedure is performed for creating a smaller aircraft footprint
onboard an aircraft carrier. Reverse rotation of the engine would
damage or create failure of brush seals such as those depicted in
FIGS. 2A and 2B.
[0010] One attempt to limit wear of brush seals is disclosed in
U.S. Pat. No. 5,026,252 to Hoffelner in which a sliding ring is
interposed between the bristle pack of the seal and the moving
element or rotor to avoid direct contact therebetween. The bristle
ends are received within a circumferential groove in the sliding
ring and are allowed to freely float or move within such groove.
Although bristle wear may be reduced in this design, it is believed
that the seal created at the interface of the sliding ring and
rotor is unsatisfactory.
[0011] Carbon seals are generally used to provide sealing of oil
compartments and to protect oil systems from hot air and
contamination. Their low leakage rates in comparison to labyrinth
or brush seals are well-suited to this application, however they
are very sensitive to pressure balances and tolerance stack-ups.
Pressure gradients at all operating conditions and especially at
low power and idle conditions must be taken into account when
considering the use of carbon seals. Seals must be designed to have
a sufficiently thick seal plate and the axial stack load path must
pass through the plate as straight as possible to prevent coning of
the seal. Another consideration with carbon seals is the potential
for seepage, weepage or trapped oil. Provisions must be made to
eliminate these conditions which may result in oil fire, rotor
vibration, and severe corrosion
[0012] According to the Advanced Subsonic Technology Initiative as
presented at the NASA Lewis Research Center Seals Workshop,
development of advanced sealing techniques to replace the current
seal technologies described above will provide high returns on
technology investments. These returns include reducing direct
operating costs by up to 5%, reducing engine fuel burn up to 10%,
reducing engine oxides of emission by over 50%, and reducing noise
by 7 dB. For example, spending only a fraction of the costs needed
to redesign and re-qualify complete compressor or turbine
components on advanced seal development can achieve comparable
performance improvements. In fact, engine studies have shown that
by applying advanced seals techniques to just a few locations can
result in reduction of 2.5% in SFC.
SUMMARY OF THE INVENTION
[0013] It is therefore among the objectives of this invention to
provide a hybrid brush seal for sealing a circumferential gap
between two relatively rotating machine components such as a rotor
and a stator which exhibits low wear rates, which provides low
leakage, which has low dependence on clearances between the rotor
and stator to retain acceptable sealing characteristics and which
has a low contamination potential.
[0014] These objectives are accomplished in a hybrid brush seal
according to this invention which comprises a number of individual
seal bristles each affixed at an outer end to the stationary
machine component or stator in an annular shape corresponding to
the circumferential gap between the stator and the rotating
component or rotor. The opposite, inner end of the seal bristles
engage one or more shoes located with respect to the rotor to
create a seal therebetween while avoiding contact of the seal
bristles with the rotor.
[0015] This invention is predicated upon the concept of employing
some of the advantages of conventional brush seals in an improved,
hybrid brush seal which overcomes typical brush seal limitations of
wear and uni-directional operation. In the presently preferred
embodiment, each of the shoes is connected at discrete points to
the abutting seal bristles such that the leading edge of the shoe
is oriented to have less contact with the rotor than the trailing
edge of the shoe. In one embodiment, each shoe is connected at two
spaced locations to the abutting seal bristles by electron beam
welding or similar mounting techniques, thus creating two hinge
points for the shoe to translate about.
[0016] In operation, the shoe functions very similarly to that of a
tilting pad bearing shoe. Prior to rotation of the rotor, the shoe
is in contact with the rotor surface. Because the leading edge of
the shoe has less contact with the rotor than its trailing edge,
when the rotor begins to rotate a hydrodynamic wedge is created
that lifts the shoe slightly off of the surface of the rotor.
Consequently, the shoe "floats" over the rotor at a design gap,
such as 0.0005 to 0.0010 inches.
[0017] The advantages of this hybrid brush seal are many. It will
have the same sealing characteristics of existing brush seals, but
will never change in performance due to bristle wear. The brush
seal backing plate can be moved further outboard of the I.D.
because the shoe will prevent the bristles from bending over in
high pressure applications. Each shoe will be designed to have a
certain amount of interference with the shaft prior to rotation.
Thus, the seal can be slightly off center during assembly but once
rotation begins, each pad will lift-off. Hence, tight tolerances
can be relaxed.
[0018] The hybrid seal can be utilized in all seal applications,
labyrinth, brush and carbon. The robust design will eliminate the
careful handling now required of carbon seals utilized in lube
system compartments. This seal may allow the engine designer to
utilize less parts in the assembly as this seal will permit "blind"
assemblies to occur.
[0019] The following table provides a comparison of the seal of the
subject invention with currently available technology.
1 Dependence Contamination Seal Type Wear Rate Leakage on
Clearances Potential Labyrinth High Low High High Seals Brush Seals
Medium Low Medium Medium Carbon Seals Medium Very Low High Low
Hybrid Seal Low Low Low Low
DESCRIPTION OF THE DRAWINGS
[0020] The structure, operation and advantages of this invention
will become further apparent upon consideration of the following
description, taken in conjunction with the accompanying drawings,
wherein:
[0021] FIGS. 1A-1E are schematic views of a number of prior art
labyrinth seals;
[0022] FIGS. 2A and 2B depict views of a prior art brush seal;
[0023] FIG. 3 is a cross sectional view of the hybrid brush seal of
this invention;
[0024] FIG. 4 is an enlarged view of a portion of the hybrid brush
seal shown in FIG. 3;
[0025] FIG. 5 is a schematic, elevational view of the seal shown in
FIGS. 3 and 4; and
[0026] FIG. 6 is a schematic, elevational view of an alternative
embodiment of the hybrid brush seal of this invention.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
[0027] Referring initially to FIGS. 3-5, the hybrid bush seal 10 of
this invention is intended to create a seal between two relatively
rotating components, namely, a fixed stator 12 and a rotating rotor
14. The seal 10 comprises a number of seal bristles 16 each having
an outer end 18 mounted to the stator 12 and an inner end 20. The
seal bristles 16 are preferably mounted to the stator 12 by
clamping, welding, brazing or other means of affixation. The seal
bristles 16 are arranged in an annular shape corresponding to the
circumferential gap between the stator 12 and rotor 14. As best
seen in FIG. 54, the seal bristles 16 extend between a low pressure
backing plate 15 and a high pressure backing plate 17 associated
with the stator 12.
[0028] In one presently preferred embodiment, the seal bristles 16
are formed of a wire material, but it is contemplated that
different materials may be utilized depending upon environmental
conditions of the particular sealing application. In the past,
brush seal materials, including the seal bristles, were chosen
primarily on their high temperature and wear capability properties.
The bristle seals 16 of this invention do not contact the rotor 14,
as discussed below, and therefore different wear characteristics
and other considerations are involved in the selection of
appropriate materials for the bristle seals 16 as compared to
conventional brush seals. The bristle seal 16 geometry may be
angled in the direction of rotation of the rotor 14 as depicted in
FIG. 3, or, alternatively, the bristle seals 16 may be straight of
have varied angles. The diameter of each bristle seal 16 can be
varied depending on the nature of the sealing environment.
Additionally, the number of seal bristles 16 can be varied with the
understanding that more bristles 16 generally leads to improved
sealing.
[0029] The outer end 18 of the seal bristles abut one or more shoes
24 located in sealing relationship to the rotor 14. In the
presently preferred embodiment, each shoe 24 is attached at
discrete locations 25 to the abutting seal bristles 16, as
illustrated in FIG. 4, such as by welding, brazing, clamping or
other means. Preferably, the leading edge 26 of each shoe 24 has
less contact with the rotor 14 than its trailing edge 28 so that a
hydrodynamic wedge is created upon rotation of the rotor 14 which
lifts the shoe 24 slightly away from the surface of the rotor 14 in
an amount equal to the design gap between the rotor 14 and stator
12. The arc length, width, height, geometry and surface
characteristics of the shoes 24 can be varied to enhance
hydrodynamic pressure between the rotor 14 and stator 12, to vary
the pressure sealing capabilities of the seal 10 and for other
purposes.
[0030] FIG. 5 illustrates how a shoe 24 captures the bristle seals
16, and it is contemplated that the shoe 24 can be wider at the
interface with rotor 14 to increase the hydrodynamic lift during
operation. Preferably, the shoes 24 are made from sheet metal
stampings or similar materials, to reduce manufacturing costs.
EXAMPLE
[0031] Considering the embodiment of the brush seal 10 of this
invention depicted in FIGS. 3-5, in one example the seal shoe has a
width of 0.10" and a length of 1.0" utilizing wire material of
Haynes-25, a wire diameter of 0.0028", a wire free length of 0.5",
a pack thickness of 0.07", a wire lay angle of 47.degree.30' and a
wire of 2450 per circumferential inch. The load per wire can be
calculated by modeling the single wire as a cantilevered beam. The
resultant load per wire depends on the amount of deflection. Per
wire the load can be between 0.0001 Lbf -0.00025 Lbf.
[0032] Thus, per inch of circumference the load could be as high as
0.6125 Lbf. The seal shoe with a width of 0.1' a length of 1.0" and
typical pressure for hydrodynamic gas bearings are between 10-25
psi. is capable of lifting off between 1.0-2.5 Lbf. Of course the
bristles will be slightly stiffer with the two hinge points and
there will be some friction on the backing plate.
[0033] The seal design will be treated very much like a tilting pad
bearing. At low rotational speeds, the pressure at the side
boundaries of the bearing pad is essentially constant and equal to
the ambient pressure, and at the pad leading and trailing edges
there is a linear pressure gradient. At high journal surface speeds
(.circle-solid.R) significant momentum changes occur at the pad
leading edge (.theta..sub.1k). Immediately upstream of the pad, the
fluid entering the pad can develop a dynamic head equal to some
fraction of a reference dynamic pressure based on the bearing
surface speed (Burton and Carper, 1967, Smalley et al., 1974, Mori
et al., 1991, Ettles et al., 1968), i.e. 1 P k ( Z , 1 k ) = 1 2 K
pP k ( R 2 ) 2
[0034] The coefficient K.sub.p is an empirical ram pressure factor.
Burton and Carper (1967) suggest a value of K.sub.p=0.64 for high
speed flows with large turbulence levels. The appearance of this
ram pressure effect due to journal rotation at the leading edge of
a bearing pad is of fundamental importance on the analysis of high
speed tilting pad bearings. This equation is simply used as a means
to show the importance of experimental/empirical validation.
[0035] The calculations from the computational model can only be as
good as the assumptions used in the analysis. Measurements of
forces and force coefficients for fixed-arc hybrid bearings with
cryogens and surrogate fluids have appeared recently. The
experimental work of Childs and Hale (1994) provides a wealth of
test results and pointed out new directives for research and uses
in the aerospace industry.
[0036] With reference now to FIG. 6, an alternative embodiment of a
hybrid brush seal 30 according to this invention is shown. The seal
30 is essentially the same as the seal 10 shown in FIGS. 3-5,
except for structure to prevent possible hysteresis within the seal
10. It is contemplated that in some circumstances in the operation
of the seal 10 of FIGS. 3-5 that high pressure acting against the
high pressure backing plate 17 could force the bristles 16 against
the low pressure backing plate 15. Such force could cause the shoes
24 to fail to follow the dynamics of the rotor 14, thus creating
seal-shoe hysteresis. The seal 30 of FIG. 6 is designed to
eliminate this potential problem by including a high pressure
backing plate 32 formed with a port 34 which extends into an
orifice 36 on the low pressure side of the seal 30. This orifice 36
extends between a low pressure backing plate 38 and the bristles
16, and is formed by an outer ring 40 mounted to one end of the low
pressure backing plate 38 and a small circumferentially extending
extension 42 on the shoes 24 which engages the opposite end of the
low pressure backing plate 36. At least some of the high pressure
gas from the high pressure side of the seal 30 bleeds into the
orifice 36 thus resisting movement of the bristles 16 against the
low pressure backing plate 38 and substantially preventing the
hysteresis effect noted above.
[0037] While the invention has been described with reference to a
preferred embodiment, it should be understood by those skilled in
the art that various changes may be made and equivalents may be
substituted for elements thereof without departing from the scope
of the invention. In addition, many modifications may be made to
adapt a particular situation or material to the teachings of the
invention without departing from the essential scope thereof.
Therefore, it is intended that the invention not be limited to the
particular embodiments disclosed as the best mode contemplated for
carrying out the invention, but that the invention will include all
embodiments falling within the scope of the appended claims.
* * * * *