Seal and bearing assembly with bearing outer portion defining seal static portion

The application relates generally to seals and, more particularly, to an assembly and method used to seal a bearing cavity containing a bearing of a gas turbine engine.

Non-contacting seals, such as labyrinth seals, are commonly used in gas turbine engines for sealing bearing cavities containing bearings secured to shafts. Such seals include a rotating part and a static part that are separated from each other by a gap, or clearance. The rotating part is secured to a shaft of the engine and the static part is usually defined by a housing supporting the bearing and defining the bearing cavity. It is desirable to minimize a height of the gap to minimize air leakage toward the bearing cavity. However, rubbing between the static and rotating parts is undesirable.

In some cases, an oil damper is used to dampen movements of the shaft relative to the housing. The oil damper allows movement between the bearing and the housing. As a consequence, the gap of the non-contacting seal must be made bigger to cater to the relative movements between the bearing and the housing such as to limit contact between the rotating and static parts of the seals. However, the bigger gap may impair the seal's efficiency. Thus, there is room for improvement.

In one aspect, there is provided a seal and bearing assembly comprising at least one bearing and at least one sealing member, the bearing configured to be received within a housing and disposed radially outwardly of a shaft relative to a rotation axis of the bearing, the bearing having an inner portion and an outer portion, the inner portion configured for rotating integrally with the shaft, the inner portion rotatable relative to the outer portion about the rotation axis, the outer portion having a protrusion extending at least in an axial direction relative to the rotation axis; an outer diameter of the outer portion sized to provide a gap between the outer diameter and the housing, the gap sized to receive a film of lubricant adapted in use to damp movements of the bearing relative to the housing, the sealing member having a rotating portion configured for rotation with the shaft radially spaced from a static portion, the static portion defined by the protrusion of the bearing outer portion.

In another aspect, there is provided a gas turbine engine comprising an engine casing extending circumferentially around a rotation axis, the engine casing defining a housing; a shaft rotatable about the rotation axis; and a seal and bearing assembly disposed between the housing and the shaft, the assembly having at least one bearing and at least one sealing member, the bearing received within a section of the housing, the bearing disposed radially outwardly of the shaft relative to the rotation axis and radially inwardly of the section of the housing, the bearing having an inner portion and an outer portion, the inner portion rotating integrally with the shaft, the inner portion rotatable relative to the outer portion about the rotation axis, the outer portion having a protrusion located radially inwardly of the section of the housing, the protrusion having a remote end axially spaced apart from the inner portion of the bearing; an outer diameter of the outer portion sized to provide a gap between the outer diameter and the housing, the gap sized to receive a film of lubricant adapted in use to damp movements of the bearing relative to the section; the sealing member having a rotating portion and a static portion, the rotating portion rotating with the shaft, the rotating portion radially spaced apart from the static portion, the static portion defined by the protrusion of the bearing outer portion.

In yet another aspect, there is provided a method of operating a seal and bearing assembly, comprising: rotating an inner portion of a bearing relative to an outer portion thereof; damping movements of the bearing relative to a housing section receiving the bearing by squeezing a film of lubricant disposed within a gap between the outer portion and the housing section; and sealing a bearing cavity from an environment outside the bearing cavity with a cooperation of a protrusion of the outer portion of the bearing and a rotating portion of a sealing member.

Reference is now made to the accompanying figures in which:

FIG. 1 is a schematic cross-sectional view of a gas turbine engine;

FIG. 2 is a schematic cross-sectional view of a seal and bearing assembly in accordance with one embodiment,

FIG. 3 is a schematic cross-sectional view of a seal and bearing assembly in accordance with another embodiment,

FIG. 4 is a schematic cross-sectional view of a seal and bearing assembly in accordance with another embodiment,

FIG. 5 is a schematic cross-sectional view of a seal and bearing assembly in accordance with another embodiment,

FIG. 6 is a schematic cross-sectional view of a seal and bearing assembly in accordance with another embodiment, and

FIG. 7 is a schematic cross-sectional view of a portion of the seal and bearing assembly of FIG. 6 .

FIG. 1 illustrates a gas turbine engine 10 of a type preferably provided for use in subsonic flight, generally comprising in serial flow communication a fan 12 through which ambient air is propelled, a compressor section 14 for pressurizing the air, a combustor 16 in which the compressed air is mixed with fuel and ignited for generating an annular stream of hot combustion gases, and a turbine section 18 for extracting energy from the combustion gases. The fan 12 , the compressor section 14 , and the turbine section 18 are rotating about a rotation axis 11 of the gas turbine engine 10 . The gas turbine engine 10 includes an engine shaft 20 and an engine casing 22 disposed circumferentially around the engine shaft 20 . The engine casing 22 is in part used to support the engine shaft 20 .

A gas turbine engine 10 such as shown in FIG. 1 can include a plurality of bearings to provide a low-friction interface between components which rotate relative to one another, such as between the engine shaft 20 the engine casing 22 . Typically, bearings may be enclosed in chambers referred to as bearing cavities, and the bearing cavities are partitioned from an environment, which can be of significantly higher pressure, by seals on each axial side.

Referring now to FIG. 2 , a seal and bearing assembly is shown at 100 . FIG. 2 , and all ensuing figures are upper views of annular components, hence the assembly portions shown in the figures have a counterpart assembly about the rotation axis 11 . However, for simplicity of the figures and to avoid a redundancy of details, the views (expect for FIG. 5 ) are limited to the upper half. The seal and bearing assembly 100 includes a bearing 30 . The bearing 30 has an inner portion 32 and an outer portion 34 . The inner portion 32 may correspond to an inner ring of the bearing 30 that is secured to the shaft 20 for integral rotation therewith. The outer portion 34 may include an outer ring 34 a of the bearing 30 . In the embodiment shown, rolling elements 36 (e.g., balls, cylinders) are received and held captive between the inner portion 32 and outer ring 34 a of the bearing 30 .

In the embodiment shown, the bearing outer portion 34 defines two annular grooves 34 b that circumferentially extend around the rotation axis 11 and face radially away from the rotation axis 11 . The grooves 34 b receive therein static seals 38 . As illustrated, the static seals 38 are piston rings, but may be O-rings, wipers, or any type of seal. The static seals 38 are compressed such that they are biased in an abutment contact with a structure surrounding said bearing outer portion 34 .

In the embodiment shown, a housing 40 extends circumferentially around the axis 11 . The housing 40 may define a chamber C that may contain lubricant. The housing 40 may be secured to the engine casing 22 or may be structurally part of the engine casing 22 . As shown, the bearing 30 is received within the housing 40 . More specifically, the housing 40 has a section 40 a that is disposed radially outwardly of the bearing 30 relative to the rotation axis 11 . The bearing 30 is received within and supported by the section 40 a of the housing 40 by being disposed radially inwardly to the section 40 a relative to the rotation axis 11 .

The assembly 100 defines a bearing cavity B that is located radially inwardly of the housing section 40 a and that may be in fluid flow communication with the housing chamber C. To limit lubricant leakage, the bearing cavity B is sealed from an environment E outside the bearing cavity B and outside the chamber C. In the embodiment shown, fore and aft sealing members 42 , 44 are disposed on opposite sides of the bearing 30 . The bearing cavity B extends axially between the fore and aft sealing members 42 , 44 and radially between the shaft and the housing section 40 a . The bearing 30 is located in the bearing cavity and axially between the sealing members 42 , 44 relative to the rotation axis 11 . The sealing members 42 , 44 are used to maintain a pressure differential between the environment E and the bearing cavity B; a pressure of the environment E being greater than a pressure of the bearing cavity B to limit lubricant from escaping out of the bearing cavity C.

Each of the sealing members 42 , 44 , which are labyrinth seals in the embodiment shown, includes rotating portions 42 a , 44 a and static portions 42 b , 44 b . Although labyrinth seals are shown, other seal types can be used, including a wiper seal, knife seal, etc. As shown, the rotating portions 42 a , 44 a are secured to the shaft 20 for integral rotation therewith. The rotating portions 42 a , 44 a define one or a plurality of knifes 42 a 1 , 44 a 1 (a plurality shown) or rims extending radially outwardly away from the shaft 20 relative to the axis 11 . The rotating portions 42 a , 44 a rotate relative to the static portions 42 b , 44 b about the axis 11 . Spacing S is defined between the rotating portions 42 a , 44 a and the static portions 42 b 44 b . The spacing S is kept small to maintain the pressure differential between the bearing cavity B and the environment E. It is understood that the knifes 42 a 1 , 44 a 1 may be defined by the static portions 42 b , 44 b rather than by the rotating portions 42 a , 44 a . Other seal configurations are contemplated.

In operation, the shaft 20 of the gas turbine engine 10 may vibrate. For example, the resulting vibrations are the result of an eccentricity of a center of mass of components (e.g., compressor, turbine) rotating with the shaft 20 relative to the rotation axis 11 . It might be advantageous to damp these vibrations, for instance, to decrease a noise level of the gas turbine engine 10 . Herein, damping means that an amplitude of the vibrations is decreased.

In the embodiment shown, an oil damper 46 is used to damp these vibrations such as to limit a propagation of the vibration from the shaft 20 and bearing 30 to the engine casing 22 . The oil damper 46 is defined by a gap G that is located radially between the bearing outer portion 34 and the section 40 a of the housing 40 . In the embodiment shown, the gap G is between the housing section 40 a and the bearing outer ring 34 a . The gap G is created by an outer diameter D 1 of the outer portion 34 that is less than an inner diameter D 2 of the housing section 40 a.

The damping effect is created by a film of lubricant F that is received within the gap G and is kept axially between the two static seals 38 . Movements of the bearing 30 relative to the housing section 40 a are dampened by the film of lubricant that absorbs at least a portion of said movement. Therefore, the film of lubricant damps movements of the bearing 30 relative to the housing 40 such that an amplitude of movements of the housing 40 may be less than an amplitude of movements of the bearing 30 or shaft 20 . The oil damper 46 may reduce transmissibility of the vibration from the engine shaft 20 to the housing 40 so that vibratory displacement of the housing 40 might be less than the vibratory displacement of the shaft 20 . The oil damper 46 might absorb the vibration energy from the shaft 20 and might reduce the amplitude of the shaft vibration. In a particular embodiment, this is beneficial for reduction of the shaft vibratory stress level, turbine 18 and compressor 14 tip clearances, aircraft cabin noise, vibration levels, and seals and bearings performance.

As illustrated, the housing 40 defines an annular groove 40 b at the housing section 40 a . The annular groove 40 b extends circumferentially around the rotation axis 11 and is used for containing lubricant. The annular groove 40 b may receive oil therein from a main pressure oil pump (not shown) of the engine 10 . The annular groove 40 b might distribute the lubricant evenly all around the oil damper gap G. The static seals 38 might limit lubricant leakage from the gap G toward the housing chamber C. The static seals 38 might be required to ensure that the gap G remains filled with lubricant all around the axis 11 . The static seals 38 might limit an amount of pressurized lubricant leakage from the oil damper 46 that might cause a reduction of a main oil pressure of the engine 10 .

It might be preferable that movements of the bearing outer portion 34 relative to the housing 40 do not affect the spacing S between the rotating and static portions 42 a , 42 b of the fore sealing member 42 . The amplitude of movements of the rotating portion 42 a of the sealing members 42 corresponds substantially to that of the shaft 20 . It might be advantageous to couple movements of the bearing 30 , which are in part due to the shaft vibrations, with movements of the static portion 42 b of the fore sealing member 42 so that an amplitude of the movements of both portions 42 a , 42 b of the fore sealing member 42 is similar. This might allow a height of the spacing S, taken in a radial direction R relative to the axis 11 , to remain more or less constant throughout vibrations of the shaft 20 .

In the embodiment shown, the static portion 42 b of the fore sealing member 42 is defined by the outer portion 34 of the bearing 30 . More specifically, the bearing outer portion 34 has a protrusion 34 c that extends at least in an axial direction A relative to the rotation axis 11 . The protrusion 34 c is located radially inwardly to the housing section 40 a relative to the rotation axis 11 . As shown, the protrusion 34 c extends away from the bearing outer ring 34 a and away from the aft sealing member 44 . The protrusion 34 c defines the static portion 42 b of the fore sealing member 42 . In the depicted embodiment, the bearing outer ring 34 a and the protrusion 34 c are integral in that they are made of a sole monoblock piece of material. As discussed herein below, other configurations are contemplated, which configurations have the static portion 42 b rigidly and directly connected to the outer ring 34 a of the bearing 30 , as opposed to being defined by the housing 40 and separated from the outer ring 34 a by the fluid gap of the oil damper 46 . In the embodiment shown, a corrosion protective coating may be applied on the static portion 42 b of the fore sealing member 42 .

Because the fore sealing member static portion 42 b corresponds to the bearing outer portion protrusion 34 c , an amplitude of the movements of the bearing inner portion 32 and of the fore sealing member rotating portion 42 a generally corresponds to that of the bearing outer portion 34 and of the fore sealing member static portion 42 b , and hence of the protrusion 34 c . In a particular embodiment, such a configuration allows the height of the spacing S to generally remain constant throughout vibrations of the shaft 20 . In a particular embodiment, and in other words, such a configuration allows the height of the spacing S between the fore sealing member static and rotating portions 42 a , 42 b to be independent of a variation of a height of the gap G taken in the radial direction.

The aft sealing member static portion 44 b is secured to the housing 40 . Hence, a spacing S between the aft sealing member rotating and static portions 44 a , 44 b may be greater than the spacing S between the fore sealing member rotating and static portions 42 a , 42 b.

In the embodiment shown, the housing section 40 a and the bearing outer portion 34 define each circumferentially spaced ventilating apertures 40 c , 34 d for ventilating the bearing cavity C. Central axes of the housing ventilating apertures 40 c might be coincident with central axes of the outer portion ventilating apertures 34 d . In the depicted embodiment, the central axes define an angle relative to the rotation axis 11 of the shaft 20 . In a particular embodiment, bearing outer ring coning caused by a thermal grading within the bearing outer portion 34 might be reduced by a cooling effect created by a passage of lubricant and air through the ventilating apertures 40 c , 34 d.

The ventilating apertures 40 c , 34 d are located axially between a remote end 34 e of the bearing outer portion 34 and the bearing outer ring 34 a . The remote end 34 e is axially spaced apart from the bearing inner portion 32 relative to the rotation axis 11 . A static seal is provided to limit lubricant leakage via a passage P between the housing 40 and the remote end 34 e . The static seal 39 is received within an annular groove 34 f defined by the protrusion 34 c . The static seal 38 is biased in an abutment contact with the housing section 40 a . The static seal 39 might reduce an amount of pressurized air leakage into the chamber C. Lubricant leakage might be prevented by having a pressure of the environment E greater than that within the bearing cavity B and housing chamber C. In the illustrated embodiment, pressurized air from the environment E enters the cavity and chamber B, C so that lubricant might not flow against a flow of pressurized air entering the cavity and chamber B, C. However, it is desirable to limit an amount of air entering the cavity and chamber B, C. The amount of pressurized air from the environment E entering the cavity and chamber B, C might be minimized by the seals 42 , 44 and the static seal 39 .

In the illustrated embodiment, an inner side of the housing section 40 a defines a lubricant collecting groove 40 d that extends circumferentially around the axis 11 . The lubricant collecting groove 40 d is axially aligned with the ventilating apertures 40 c and is in fluid flow communication with said ventilating apertures 40 c . The collecting groove 40 d is used for accumulating and draining lubricant through the ventilating apertures 40 c . The lubricant collecting groove 40 d receives pressurized lubricant from the engine main pressure oil pump (not shown). The groove 40 d might distribute the lubricant evenly all around the oil damper gap G. The ventilation apertures 40 c and 34 d provide fluid communication between a portion of the bearing cavity B that is axially forward of the bearing 30 with the housing chamber C so that lubricant might escape from this portion of the bearing cavity B into the housing chamber C. This might preclude the lubricant from overheating and hence might preclude oil coking. By gravity, the lubricant is collected at a bottom of the housing chamber C from where this lubricant might be scavenged through an oil scavenge tube (not shown).

During operation, the bearing 30 requires lubrication. In the embodiment shown, a scoop 50 is secured to the shaft 20 for integral rotation therewith and is located adjacent the bearing 30 . In rotation, the scoop 50 is used for receiving the lubricant. The scoop 50 may have grooves 50 a that, with the shaft 20 , define together circumferentially spaced channels 50 b that are tapered such that a centrifugal force pushes the lubricant that has been received by the scoop 50 in the axial direction A relative to the axis 11 toward the bearing 30 .

An inner side of the bearing inner portion, or inner ring, 32 may have grooves 32 a that extend in the axial direction. The grooves 32 a are circumferentially spaced and cooperate with the shaft 20 in defining circumferentially spaced channels 32 b that are configured for receiving lubricant therein. The inner ring channels 32 b are in fluid flow communications with the scoop channels 50 b . As shown, each of the inner ring channels 32 b is in fluid communication with a respective one of circumferentially spaced radial conduits 32 c that are defined through the bearing inner portion 32 . The radial conduits 32 c are fluidly connected to a volume defined by the bearing inner portion 32 and that is configured for rollingly receiving the bearing rolling elements 36 .

Once the lubricant is trapped by the scoop 50 , it may flow within the scoop channels 50 b toward the bearing 30 , to then flow within the bearing inner ring channels 32 b toward the radial conduits 32 c , and then flow within the radial conduits 32 c for being routed in the volume.

As for the scoop channels 50 b , the bearing inner ring channels 32 b may be tapered such that a radial depth increases in the axial direction A toward the radial conduits 32 c . In rotation, the tapering of the channels 50 b , 32 b combined with centrifugal force push the lubricant toward the radial conduits 32 c . Once the lubricant enters the radial conduit 32 c , the centrifugal force pushes the lubricant radially away from the shaft 20 to feed the lubricant to the volume containing the bearing rolling elements 36 .

In the embodiment shown, the bearing outer portion 34 may include a bearing squirrel cage 34 g that is secured to the housing 40 . The bearing squirrel cage 34 g defines openings 34 h that are circumferentially spaced around the axis 11 . The bearing squirrel cage 34 g is used for providing flexibility. More specifically, the squirrel cage 34 g allows radial movement of the bearing outer ring 34 a relative to the housing 40 . The squirrel cage 34 g consists of plurality of the axial beams 34 g 1 located between adjacent openings 34 h and that connect the bearing outer ring 34 a with a bearing flange 34 m that extends radially outwardly from an axially rearward end of the squirrel cage 34 g . The bearing flange 34 m might be rigidly attached to the housing 40 (e.g., by bolts). When radial movements of the shaft 20 occur (e.g., vibration), the bearing inner ring 32 might move together with the shaft 20 and might push the rolling elements 36 , which might push the outer ring 34 a . The squirrel cage beams 34 g 1 might bend. Bending stiffness of the squirrel cage beams 34 g 1 is selected to maintain highest possible efficiency of the oil damper 46 . The squirrel cage 34 g and the bearing outer ring 34 a might be integral for instance by being made from a same piece of material. Other configurations are contemplated.

Referring now to FIG. 3 , another embodiment of a seal and bearing assembly is shown at 200 . For the sake of conciseness, only elements that are different than those described with respect to the assembly of FIG. 2 are described herein below.

In the embodiment shown, the bearing outer portion 134 includes the bearing outer ring 134 a and the protrusion 134 c . The bearing outer ring 134 a defines a tab 134 i that extends at least in the axial direction, whereby the bearing outer ring 134 a and the protrusion 134 c are rigidly connected for concurrent movement. The protrusion 134 c is secured to the bearing outer ring tab 134 i . In the embodiment shown, the protrusion 134 c and the tab 134 i are maintained secured with each other via a tight fit engagement therebetween. Other configurations are contemplated.

In such an embodiment, the bearing outer ring tab 134 i define circumferentially spaced ventilating apertures 134 j that are aligned with the ventilating apertures 134 d of the protrusion 134 c and the apertures 140 c of the housing section 140 a . Central axes of the tab ventilating apertures 134 j might be coincident with central axes of apertures 134 d , 140 c of the protrusion 134 c and housing 140 .

To maintain an axial position of the protrusion 134 c relative to the bearing outer ring 134 a , the housing 140 defines an axial retention shoulder 140 e . The shoulder 140 e extends radially inwardly toward the shaft 20 . As illustrated, axial movements of the bearing protrusion 134 c relative to the bearing 130 are limited by a cooperation of the housing shoulder 140 e and the bearing outer ring 134 a.

In the depicted embodiment, a rotation of the bearing outer ring 134 a relative to the protrusion 134 c is limited by slots and lugs arrangements 154 that are circumferentially distributed around the rotation axis 11 . Other configurations are contemplated.

Referring now to FIG. 4 , another embodiment of a seal and bearing assembly is shown at 300 . For the sake of conciseness, only elements that are different than those described with respect to the assembly of FIGS. 2-3 are described herein below. In the embodiment shown, the lubricant collecting groove 240 d that is defined through the housing section 240 a of the housing 240 is provided in the form of two conical slopes 240 d 1 that converge toward the central axes of the housing ventilating apertures 240 d . Similarly to the groove 140 d of the embodiment of FIG. 3 , the present groove 240 d is used to collect lubricant and to guide said lubricant toward the ventilating apertures 240 d . In a particular embodiment, a risk of lubricant coking near the static seals 38 is reduced by collecting and draining oil via the ventilating apertures 240 c compared to a configuration lacking such groove 240 d or a configuration having a rounded groove as the one illustrated in FIG. 3 .

Referring now to FIG. 5 , another embodiment of a seal and bearing assembly is shown at 400 . For the sake of conciseness, only elements that are different than those described with respect to the assembly of FIG. 3 are described herein below.

In the embodiment shown, sealing between the housing section 340 a and the bearing outer portion protrusion 334 c is provided by minimizing axial gaps 360 . More specifically, the housing section 340 a defines two radial tabs 340 f extending in the radial direction R toward the shaft 20 . The bearing protrusion 334 c defines a radial tab 334 k that extends in the radial direction R away from the shaft 20 .

A first one of the axial gaps 360 is defined axially between a first one of the housing section radial tabs 340 f and by the radial tab 334 k of the bearing protrusion 334 c . A second one of the axial gaps 360 is defined axially between a remote end 3341 of the bearing outer ring tab 334 i and a second one of the housing section radial tabs 340 f . The first and second axial gaps 360 are axially offset from each other relative to the axis 11 .

In the depicted embodiment, the first of the axial gaps 360 has tighter tolerance control than the second one of the axial gaps 360 to limit an air flow coming into the bearing cavity C from the environment E outside the bearing cavity C. This tight tolerance might be achieved by precise machining of parts or by having a sealing member static portion of higher length than illustrated.

In the embodiment shown, two chambers 362 are defined within the passage P located radially between the bearing protrusion 334 c and the housing section 340 a and that extend circumferentially around the rotation axis 11 . A first one of the two chambers 362 extends between the axial gaps 360 . A second one of the two chambers 362 extends between the second one of the axial gaps 360 and the bearing outer ring 334 a . The ventilating apertures 340 d of the housing section 340 a fluidly connect the second one of the chambers 362 to the bearing cavity C.

As shown, the ventilating apertures 340 d of the housing section 340 a are offset from the apertures 334 j , 334 d of the bearing outer ring tab 334 i and protrusion 334 c . It is understood that the bearing outer ring tab 334 i and protrusion 334 c may be unitary without departing from the scope of the present disclosure.

In the embodiment shown, the housing section 340 a defines a drain hole 364 that fluidly connects the first one of the chambers 362 to the bearing cavity C so that excess lubricant may be flushed out of the first of the chambers 362 when air pressure increases. The drain hole 364 is located on a lower halve of the housing 340 such that the lubricant flows toward said hole 364 by gravity.

In a particular embodiment, using axial gaps instead of static seals (e.g., piston rings, O-rings) eliminates wear that would otherwise occur with static seals. Hence, the assembly having axial gaps might require less maintenance than an assembly with static seals.

Referring now to FIGS. 6-7 , another embodiment of a seal and bearing assembly is shown at 500 . For the sake of conciseness, only elements that are different than that described with respect to the assembly of FIG. 2 are described herein below.

In the embodiment shown, the bearing outer portion 434 includes the bearing outer ring 434 a and a two-sided protrusion 434 c that extends circumferentially around the rotation axis 11 . The bearing outer ring 434 a is disposed radially inwardly to the two-sided protrusion 434 c and the axial gap G is defined between the two-sided protrusion 434 c and the housing section 440 a.

As illustrated, the static portions 442 b , 444 b of each of the two sealing members 442 , 444 are defined by the two-sided protrusion 434 c . More specifically, the two-sided protrusion 434 c defines a fore section 434 c 1 and an aft section 434 c 2 extending on opposite sides of the bearing 430 and both extending at least in the axial direction A in opposite direction away from the bearing outer ring 434 a . The rear protrusion 434 c 2 defines circumferentially spaced apertures 434 c 3 that are configured to allow lubricant ejected from a nozzle 466 to flow toward the scoop 50 .

In the depicted embodiment, a rotation of the bearing outer ring 434 a relative to the two-sided protrusion 434 c is limited by slot and lug arrangements 454 that are circumferentially distributed around the rotation axis 11 . Other configurations are contemplated. As shown, the slot and lug arrangements 454 are located on a rear side of the bearing outer ring 434 a . To limit an axial movement of the two-sided protrusion 434 c relative to the bearing outer ring 434 a , a retaining ring 468 is located at the fore section 434 c 1 of the protrusion 434 c and is received within an annular groove 434 c 4 defined by the protrusion fore section 434 c 1 . The retaining ring 468 protrudes radially inwardly so that it abuts axially against the bearing outer ring 434 a.

Referring more particularly to FIG. 7 , to limit an airflow between the housing 440 and the two-sided protrusion 434 c , two seals 470 are used, only one of which is described herein below as they are, in the embodiment shown, identical.

The seal 470 includes a static seal 470 a (e.g., piston ring) and a biasing member 470 b (e.g., wave spring). As shown, the static seal 470 a and the biasing member 470 b are disposed axially between a retaining ring 472 , which is received within a groove 440 g defined by the housing 440 , and the fore section 434 c 1 . The biasing member 470 b is used to push on the static seal 470 a to create an abutment contact between the fore section 434 c 1 and the static seal 470 a.

The vibrations discussed herein above might cause the static seal 470 a , which may be made of a softer material than that of the two-sided protrusion 434 c , to wear with time. To cater to this wear, the static seals 470 a define a wearable nose 470 a 1 that is designed to wear way with time. As the wearable nose 470 a 1 wears, the static seal 470 a moves axially toward the two-sided protrusion 434 c because it is pushed by the biasing member 470 b . At some point, the wearable nose 470 a 1 is sufficiently worn away such that the static seal 470 a abut against a radial shoulder 440 h of the housing 440 . Stated otherwise, the radial shoulder 440 h acts as a stopper. At this time, a contact pressure between the static seal 470 a and the protrusion 434 c decreases and the wearable nose might stop to wear. At this point, the static seal 470 a is worn-in and might keep a zero gap between the static seal 470 a and the two-sided protrusion 434 c to maintain a sealing function.

Referring to FIG. 2 , for operating the seal and bearing assembly 100 , the inner portion 32 of the bearing 30 is rotated relative to the outer portion 34 thereof. Movements of the bearing 30 relative to the housing section 40 a are damped by squeezing a film of lubricant disposed within the gap G between the bearing 30 and the housing section 40 a . The bearing cavity C is sealed with a cooperation of the protrusion 34 c of the outer portion 34 of the bearing 30 and the rotating portion 42 a of the fore sealing member 42 .

In the embodiment shown, fluid flow communication between the bearing cavity C and the environment E outside the bearing cavity C is limited by sealing the passage P, which is located between the housing 40 and the protrusion 34 , from the environment E.

As shown in FIG. 5 , fluid flow communication between the environment E and the bearing cavity C, within the passage P, is limited by constricting said passage with the axial gaps 360 that are located between the housing 340 and the protrusion 334 c.

As shown in FIG. 6 , the bearing cavity C is sealed from the environment E on opposite sides of the bearing 30 with the cooperation of the aft section 434 c 2 of the two-sided protrusion 434 c and the fore section 434 c 1 of the two-sided protrusion 434 c with respective rotating portions 442 a , 444 a of the sealing members 442 . 444 .

The above description is meant to be exemplary only, and one skilled in the art will recognize that changes may be made to the embodiments described without departing from the scope of the invention disclosed. Still other modifications which fall within the scope of the present invention will be apparent to those skilled in the art, in light of a review of this disclosure, and such modifications are intended to fall within the appended claims.