U.S. patent application number 10/832053 was filed with the patent office on 2004-11-04 for hydrodynamic brush seal.
Invention is credited to Justak, John F..
Application Number | 20040217549 10/832053 |
Document ID | / |
Family ID | 33313623 |
Filed Date | 2004-11-04 |
United States Patent
Application |
20040217549 |
Kind Code |
A1 |
Justak, John F. |
November 4, 2004 |
Hydrodynamic brush seal
Abstract
A hybrid brush seal is provided having two bundles of axially
spaced seal bristles each of which are mounted in a ring shape on a
first machine component with bristle ends directed at a sealing
surface of the second, rotating machine component. 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 separates the shoe(s) from the shaft.
The shoe(s) is attached to the bristle ends at discreet locations.
Alternatively, one or more bundles of seal bristles are mounted at
one end either to the fixed or rotating machine component, with the
opposite bristle ends directed toward one or more shoes, and
wherein one or more spring elements are connected between the
machine component and shoes.
Inventors: |
Justak, John F.; (Stuart,
FL) |
Correspondence
Address: |
HOLLAND & KNIGHT, LLP
ONE EAST BROWARD BLVD.
SUITE 1300
FT LAUDERDALE
FL
33301
|
Family ID: |
33313623 |
Appl. No.: |
10/832053 |
Filed: |
April 26, 2004 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
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60466979 |
May 1, 2003 |
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Current U.S.
Class: |
277/355 |
Current CPC
Class: |
F16J 15/3288 20130101;
F01D 11/00 20130101; F16J 15/441 20130101; F05D 2240/56 20130101;
F01D 11/02 20130101; F16J 15/164 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 about a longitudinal axis,
comprising: a first bundle of seal bristles each having a first end
and a second end, said first ends of said first bundle of seal
bristles being mounted to one end of said first and second machine
components and said second ends thereof extending in a direction
toward the other of said first and second machine components; a
second bundle of seal bristles each having a first end and a second
end, said first ends of said second bundle of seal bristles being
mounted to one of said first and second machine components and said
second ends thereof extending in a direction toward the other of
such first and second machine components, said second bundle of
seal bristles being axially spaced from said first bundle of seal
bristles; at least one shoe extending about whichever one of the
first or second machine components is located opposite said first
ends of said seal bristles, said at least one shoe being fixed to
said second ends of each of said first bundle and said second
bundle of seal bristles in at least one location therealong to
substantially prevent relative movement between said at least one
shoe and said second ends and so that said seal bristles do not
directly contact either of the first and second machine
components.
2. The brush seal of claim 1 in which said first ends of said first
bundle of seal bristles and said first ends of said second bundle
of seal bristles are mounted to the first machine component.
3. The brush seal of claim 1 in which said second ends of said
first bundle of seal bristles and said second ends of said second
bundle of seal bristles extend in a direction toward the second
machine component.
4. The brush seal of claim 1 further including a high pressure
backing plate, a low pressure backing plate and at least one spacer
plate located between said high and low pressure backing plates,
said first group of seal bristles being located between said high
pressure backing plate and said at least one spacer plate and said
second group of seal bristles being located between said at least
one spacer plate and said low pressure backing plate.
5. The brush seal of claim 1 in which said at least one shoe is
formed with a flow path for balancing static pressure.
6. 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 about a longitudinal axis,
comprising: a bundle of seal bristles each having a first end and a
second end, said first ends of said bundle of seal bristles being
mounted to one of said-first and second machine components and said
second ends thereof extending in a direction toward the other of
said first and second machine components; at least one spring
element having a first end connected to one of said first and
second machine components and a second end extending in a direction
toward the other of said first and second machine components; and
at least one shoe extending about one of said first or second
machine components, said at least one shoe being fixed to whichever
one of said first and second ends of said spring element is located
opposite said first ends of said seal bristles, said at least one
shoe preventing said second ends of said seal bristles from
directly contacting either said first or second machine
component.
7. The brush seal of claim 6 in which said at least one spring
element is resilient in the radial direction and stiff in the axial
direction.
8. The brush seal of claim 6 in which said at least one spring
element includes a first spring element and a second spring element
which is axially spaced from said first spring element.
9. The brush seal of claim 6 in which said at least one spring
element is formed of a strip of spring steel.
10. The brush seal of claim 6 in which said at least one spring
element is a beam having radially spaced inner and outer bands, one
end of each of said inner and outer bands being connected to one of
the first and second machine components and the other end of said
inner and outer bands being connected to said at least one
shoe.
11. The brush seal of claim 6 in which said at least one shoe is
formed with a flow path for balancing static pressure.
12. 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 about a longitudinal axis,
comprising: a first bundle of seal bristles each having a first end
and a second end, said first ends of said first bundle of seal
bristles being mounted to one of said first and second machine
components and said second ends thereof extending in a direction
toward the other of said first and second machine components; a
second bundle of seal bristles each having a first end and a second
end, said first ends of said second bundle of seal bristles being
mounted to one of said first and second machine components and said
second ends thereof extending in a direction toward the other of
said first and second machine components, said second bundle of
seal bristles being axially spaced from said first bundle of seal
bristles; at least one spring element having a first end connected
to one of the first and second machine components and a second end
extending in a direction toward the other of said first and second
machine components; and at least one shoe extending about whichever
one of the first or second machine component is located opposite
said first ends of said seal bristles, said at least one shoe being
fixed to said second end of said spring element, said at least one
shoe preventing said second ends of said seal bristles of each of
said first and second bundles from directly contacting either the
first or second machine component.
13. The brush seal of claim 12 further including a high pressure
backing plate, a low pressure backing plate and at least one spacer
plate located between said high and low pressure backing plates,
said first bundle of seal bristles being located between said high
pressure backing plate and said at least one spacer plate and said
second group of seal bristles being located between said at least
one spacer plate and said low pressure backing plate.
14. The brush seal of claim 12 in which said at least one spring
element is resilient in the radial direction and stiff in the axial
direction.
15. The brush seal of claim 12 in which said at least one spring
element includes a first spring element and a second spring element
which is axially spaced from said first spring element.
16. The brush seal of claim 12 in which said at least one spring
element is formed of a strip of spring steel.
17. The brush seal of claim 12 in which said at least one spring
element is a beam having radially spaced bands, one end of each of
said inner and outer bands being connected to one of the first and
second machine components and the other end of said inner and outer
bands being connected to said at least one shoe.
18. The brush seal of claim 12 in which said at least one shoe is
formed with a flow path for balancing static pressure.
Description
[0001] This application claims priority under 35 U.S.C. .sctn.
119(e) to U.S. Provisional Application Serial No. 60/466,979 filed
May 1, 2003 for all commonly disclosed subject matter. U.S.
Provisional Application Serial No. 60/466,979 is expressly
incorporated herein by reference in its entirety to form a part of
the present disclosure.
FIELD OF THE INVENTION
[0002] 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 two sets of axially
spaced seal bristles each of which are mounted in a ring shape on a
first machine component with bristle ends directed at sealing
surface of the second, rotating machine component. 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 separates the shoes from the shaft. The
shoe(s) is attached to the bristle ends at discreet locations.
Alternatively, one or more sets of seal bristles are mounted at one
end either to the fixed or rotating machine component, with the
opposite bristle ends directed toward one or more shoes, and
wherein one or more spring elements are connected between the
machine component and shoes.
BACKGROUND OF THE INVENTION
[0003] 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.
[0004] 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 being 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.
[0005] 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.
[0006] 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.
[0007] 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.
[0008] 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. 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.
[0009] 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.
[0010] An improvement of prior brush seals, including that
disclosed in the '252 patent to Hoffelner noted above, is found in
my U.S. Pat. No. 6,428,009. In that design, one end of each of a
plurality of seal bristles is fixed in an annular shape and mounted
to the fixed machine component or stator while their opposite ends
are attached to a number of individual shoes located proximate the
rotating machine component or rotor. 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. 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. It has been found that one limitation of
the design disclosed in the '009 patent is a potential problem with
"roll over" under pressure load, i.e. the shoes can tip or pivot in
the axial direction thus creating a leakage path.
[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. Carbon 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] A hybrid brush seal is provided which is generally similar
to the one disclosed in my prior U.S. Pat. No. 6,428,009, but which
overcomes the tendency of the shoes to roll over under the
application of a pressure load.
[0014] In one presently preferred embodiment, two sets or bundles
of seal bristles are axially spaced from one another, i.e. in the
direction of the longitudinal axis of two relatively rotating
machine components such as the rotor and stator of a gas turbine
engine. One end of the seal bristles in each bundle is fixed in an
annular shape to either the stator or the rotor, while the opposite
end of the seal bristles in each bundle extends to one or more
shoes circumferentially disposed about the other machine component.
The shoes are located with respect to the rotor or stator to
created a seal between the two while avoiding contact of the seal
bristles with the relatively rotating component. Each of the shoes
is connected at discrete points to the end of the seal bristles
such that the leading edge of the shoe is oriented to have less
contact with the rotor or the stator 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.
[0015] In an alternative embodiment, one or more bundles or seal
bristles are mounted at one end to either the rotor or the stator,
and their opposite end extends toward one or more shoes located
proximate the other of the rotor or stator. A spring element is
connected between the shoes and the rotor or stator which is
flexible in the radial direction, but axially stiff. The spring
element functions to assist in preventing roll over of the shoes
with respect to the rotor or stator where it is located, thus
maintaining an effective seal under pressure load. It is
contemplated that the ends of the seal bristles proximate the shoes
can be either connected to the shoes such as by welding or other
means of attachment, or spaced from the shoes. In either case, the
seal bristles act as a secondary seal between the rotor and stator
in combination with the shoes.
[0016] In operation, the shoes of either embodiment of this
invention function very similarly to that of a tilting pad bearing
shoe. Prior to rotation of the rotor, the shoe is in contact with
the rotor or stator surface. Because the leading edge of the shoe
has less contact with the rotor or stator 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 or
stator. Consequently, the shoe "floats" over the rotor or stator at
a design gap, such as 0.0005 to 0.0010 inches.
[0017] The advantages of the hybrid brush seal of this invention
are many. It has 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 prevents the bristles from bending over in
high pressure applications. Each shoe may have a certain amount of
interference with the rotor or stator 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 of this invention can be utilized in all
seal applications, including labyrinth, brush and carbon. The
robust design eliminates 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 one embodiment of the
hybrid brush seal of this invention;
[0024] FIG. 4 is a schematic, elevational view of the seal shown in
FIG. 3;
[0025] FIG. 5 is a view similar to FIG. 4, except of an alternative
embodiment herein;
[0026] FIG. 6 is a schematic, elevational view of an alternative
embodiment of the seal herein employing a single bundle of seal
bristles and axially spaced spring elements;
[0027] FIG. 7 is a view similar to FIG. 6, except employing two
sets of axially spaced seal bristles;
[0028] FIG. 8 is a cross sectional view of a still further
embodiment of the brush seal of this invention; and
[0029] FIG. 9 is a cross sectional view taken generally along line
9-9 of FIG. 8.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
[0030] 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. In this embodiment, the seal 10 comprises a first group or
bundle 16 of seal bristles 18 and a second bundle 20 of seal
bristles 18 which are axially spaced from the first bundle 16. As
used herein, the term "axial" or "axially spaced" refers to a
direction along the longitudinal axis of the stator 12 and rotor
14, e.g. axis 22 in FIG. 3, whereas "radial" refers to a direction
perpendicular to the longitudinal axis 22.
[0031] The seal bristles 18 in each bundle 16 and 20 have an inner
end 24 and an outer end 26. In the embodiment illustrated in FIGS.
3 and 4, the outer end 26 of the seal bristles 18 in each bundle
16, 20 is affixed to the stator 12. For purposes of the present
discussion, the construction and operation of the seal 10 herein is
described with the seal bristles 18 in that orientation. It should
be understood, however, that the inner end 24 of the seal bristles
18 could be affixed to the rotor 14. Preferably, the seal bristles
18 are mounted to the stator 12 or rotor 14 by clamping, welding,
brazing or other means of affixation. The seal bristles 18 in each
bundle 16 and 20 are arranged in an annular shape corresponding to
the circumferential gap between the stator 12 and rotor 14. As best
seen in FIGS. 4 and 5, a spacer plate 28 is located in the axial
space between the seal bristle bundles 16 and 20. The seal bristles
18 in bundle 16 are captured between a high pressure backing plate
30 associated with the stator 12 and the spacer plate 28, whereas
the seal bristles 18 in bundle 20 extend between a second spacer
plate 31 and a low pressure backing plate 32.
[0032] In one presently preferred embodiment, the seal bristles 18
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 for their high temperature and wear capability
properties. The bristle seals 18 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 18 as
compared to conventional brush seals. The bristle seal 18 geometry
may be angled in the direction of rotation of the rotor 14, or,
alternatively, the bristle seals 18 may be straight and have varied
angles. The bristle seals 18 may be round, square, rectangular. or
other shapes, and, if round, the diameter of each bristle seal 18
can be varied depending on the nature of the sealing environment.
The outer end 26 of the bristle seals 18 in each bundle 16 and 20
may be fused together or free to move independently. Further, the
number of seal bristles 18 within each bundle 16 and 20 can be
varied with the understanding that more seal bristles 18 generally
leads to improved sealing.
[0033] The inner end 24 of the seal bristles 18 in each bundle abut
one or more shoes 34 located in sealing relationship to the rotor
14. In the embodiment of FIG. 4, the shoes 34 are formed with
axially spaced ridges 36 and 38. One side of the bundle 16 of seal
bristles 18 abuts the ridge 36, and one side of the bundle 20 of
seal bristles 18 abuts the ridge 38. FIG. 5 depicts a slightly
different construction of shoes 34 in which the ridge 36 is the
same as that in FIG. 4, but a ridge 40 is formed on the shoes 34 in
position to contact the opposite side of the bundle 20 of seal
bristles 18 compared to the FIG. 4 embodiment. In both cases, each
shoe 34 is attached at discrete locations to the abutting seal
bristles 18 such as by welding, brazing, clamping or other means.
The arc length, width, height, geometry and surface characteristics
of the shoes 34 can be varied to enhance hydrodynamic pressure
between the rotor 14 and stator 12, to balance the static pressures
within the system to vary the pressure sealing capabilities of the
seal 10 and for other purposes. Preferably, the shoes 34 are made
from sheet metal stampings or similar materials, to reduce
manufacturing costs.
[0034] Referring now to FIGS. 6-9, alternative embodiments of a
brush seal of this invention are shown. In FIG. 6, a brush seal 40
is shown in which a single bundle 42 of seal bristles 18 is located
between a high pressure backing plate 44 and a low pressure backing
plate 46. For purposes of the present discussion, and consistent
with the description of the previous embodiments, an outer end 48
of each seal bristle 18 in bundle 42 is mounted to the stator 12
while the inner end 50 extends toward the rotor 14. It should be
understood that the seal bristles 18 in bundle 42 could be affixed
to the rotor 14 instead of the stator 12.
[0035] In the embodiments of FIGS. 3-5, axial rigidity and radial
compliance of the seal 10 is provided by the seal bristles 18 in
the bundles .16 and 20 through their connection between the stator
12. and shoes 34. In the embodiment of FIG. 6, the seal bristles 18
in the bundle 42 need not be connected to a shoe 34. Instead, a
spring element 52 is connected between the high pressure backing
plate 44 and the shoe 34, and another spring element 54 is
connected between the low pressure backing plate 46 and the shoe
34. These spring elements 52 and 54 are axially spaced from one
another and provide essentially the same resistance to roll over of
the seal 40 as the bundles 16 and 20 of seal bristles 18 in the
seal 10 of FIGS. 3-5. Preferably, the spring elements 52 and 54 are
formed of spring steel or other material which is flexible in the
radial direction but stiff in the axial direction.
[0036] The embodiment of FIG. 7 depicts a seal 55 which is similar
to the seal 40 of FIG. 6, except that two axially spaced bundles 56
and 58 of seal bristles 18 are employed instead of one. The bundle
56 of seal bristles 18 is retained between a low pressure backing
plate 60 and a spacer plate 62, whereas the bundle 58 is retained
between a second spacer plate 64 and a high pressure backing plate
66. As in the embodiment of FIG. 6; the bristles 18 of each bundle
56, 58 need not be connected to a shoe 34. Axial rigidity and
radial compliance are provided primarily by a spring element 68
connected between the low pressure backing plate 60 and shoe 34,
and a second spring element 70 connected between the high pressure
backing plate 66 and the shoe 34.
[0037] Referring now to FIGS. 8 and 9, a still further embodiment
of a seal 72 according to this invention is shown. The seal 72 is
similar to that of seals 40 and 55 except for the spring elements
74. Each spring element 74 is essentially a rectangular-shaped beam
with an outer band 76 radially spaced from an inner band 78. One
end of each of the bands 76 and 78 is connected to a seat 80 formed
in the stator 12, and the opposite end of bands 76, 78 mounts to a
ridge 82 formed in a shoe 34. The spring element 74 functions to
maintain the shoe 34 is sealing relationship with the rotor 14 in
the same manner as the spring elements 52, 54 and 68, 70. A bundle
72 of seal bristles 18 is fixed at its outer end to the stator 12,
and the inner end of each seal bristle 18 extends toward the shoe
34 where it may or may not be affixed thereto.
[0038] In each of the embodiments of FIGS. 6-9, the seal bristles
18 form essentially a secondary seal. The shoes 34 are maintained
in position with respect to the stator 12 and rotor 14 by the
spring elements 52 and 54, 68 and 70, and 74, which cooperate with
the bristle bundles to resist roll over.
[0039] 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.
[0040] For example, it has been found advantageous to provide a
flow path in the shoes 34 of this invention to assist in balancing
static pressure in the system. This flow path can take the form of
a step 84 formed in the shoe 34, as depicted in FIG. 6.
[0041] 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.
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