WO2014143097A1 - Joint circonférentiel avec patin en céramique - Google Patents

Joint circonférentiel avec patin en céramique Download PDF

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Publication number
WO2014143097A1
WO2014143097A1 PCT/US2013/040812 US2013040812W WO2014143097A1 WO 2014143097 A1 WO2014143097 A1 WO 2014143097A1 US 2013040812 W US2013040812 W US 2013040812W WO 2014143097 A1 WO2014143097 A1 WO 2014143097A1
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WO
WIPO (PCT)
Prior art keywords
ring
ceramic runner
seal
sealing
carrier
Prior art date
Application number
PCT/US2013/040812
Other languages
English (en)
Inventor
Thurai Manik Vasagar
Original Assignee
Stein Seal Company
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Stein Seal Company filed Critical Stein Seal Company
Priority to US14/130,511 priority Critical patent/US20140265151A1/en
Publication of WO2014143097A1 publication Critical patent/WO2014143097A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/28—Selecting particular materials; Particular measures relating thereto; Measures against erosion or corrosion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/003—Preventing or minimising internal leakage of working-fluid, e.g. between stages by packing rings; Mechanical seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F01D25/183—Sealing means
    • F01D25/186—Sealing means for sliding contact bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/06—Arrangements of bearings; Lubricating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/28—Arrangement of seals
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/20—Oxide or non-oxide ceramics

Definitions

  • the invention generally relates to a sealing device for turbine engines.
  • the invention is directed to a circumferential seal disposed about a rotatable shaft wherein a ceramic runner is attached to the shaft adjacent to a carbon sealing ring.
  • Seal assemblies are used in gas turbine engines to prevent or limit leakage of a fluid along the interface between a rotating shaft and an otherwise fixed element.
  • FIG. 1 shows a typical circumferential seal 1 including a rotating component called a seal rotor 2 and a non-rotating component called a seal stator 3.
  • the seal rotor 2 is made of metal, is mounted to a rotatable shaft 4, and has a radially outward facing sealing surface 5.
  • the seal stator 3 includes a ring 6 made of metal mounted to the housing 7 and a sealing ring 8.
  • the sealing ring 8 is made of carbon and includes an inward facing sealing surface 10.
  • the seal stator 3 and seal rotor 2 are arranged so that the inward facing sealing surface 10 circumscribes the outward facing sealing surface 5.
  • a small radial gap 9 is maintained between the sealing ring 8 and seal rotor 2 to avoid damage to the softer sealing ring 8.
  • a common problem associated with circumferential seals and bushings occurs as a result of variation in the radial gap 9 between the sealing ring 8 and seal rotor 2. This variation is due in part to the mechanical growth of the seal rotor 2 due to centrifugal effects, but more significantly due to a disparity in the thermal growth between the seal rotor 2, typically composed of a material with a higher coefficient of thermal expansion, and the sealing ring 8, typically composed of a material with a lower coefficient of thermal expansion.
  • a variation in the radial gap 9 produces an undesirable effect when it is too wide open or too narrow. If the radial gap 9 is too large, then the flow of fluid between the sealing ring 8 and the seal rotor 2 increases so as to adversely affect pressures within the high and low pressure sections of a turbine engine, thereby reducing the performance and efficiency thereof. If the gap is too small, then contact between the sealing ring 8 and seal rotor 2 occurs and damage results to one or both components.
  • a section 11 of a gas turbine engine including a rotatable shaft 4 on which rotating engine components, such as the radial compressor wheel 12, are mounted.
  • a stationary housing 7 Circumscribing the rotatable shaft 4 is a stationary housing 7.
  • the stationary housing 7 is mounted atop a bearing 13 having an inner race 14 which is mounted on the rotatable shaft 4.
  • Disposed between the housing 7 and shaft 4 is a circumferential seal 15.
  • the circumferential seal 15 includes a seal stator 3 having a metal ring 6 mounted to the housing 7 and a carbon sealing ring 8 mounted to its radial inward facing surface.
  • the carbon sealing ring 8 has a radially inward facing sealing surface 10.
  • the circumferential seal 15 also includes a sealing rotor 16.
  • the rotor 16 includes a ceramic runner 17 having a radially outward facing sealing surface 5 in rubbing contact with the radially inward facing sealing surface 10 of the sealing ring 8 to control leakage across the radial gap 9.
  • the runner 17 has a radially outward extending fiange 18.
  • the runner 17 has a radially inward extending fiange 19 having axial faces adapted to receive an axial clamping load.
  • the sealing rotor 16 further includes two metallic annular clamping members 20, 21 for providing this clamping load.
  • the first annular clamping member 21 includes a cylindrical portion 22 having a radially inward extending fiange 23 at one end and a radially outward extending lip 24 at the other end.
  • the length and thickness of the cylindrical portion 22 are selected to impart radial flexibility to the annular clamping member 21 so that the cylindrical portion 22 acts as a cantilevered beam rigidly fixed at the inward extending flange 23.
  • the second annular clamping member 20 has a cylindrical portion 25 with a radially inward extending flange 26 at one end and an axial face 27 at the other end.
  • the cylindrical portion 25 has a plurality of circumferentially extending slots (not shown) that impart axial flexibility to the cylindrical portion 25 allowing it to compress and expand like a coil spring.
  • the ceramic runner 17 is flexibly clamped between the axial face 27 and outward extending lip 24.
  • the circumferential seal 15 provides substantially improved sealing efficiency over metal seal rotors 2 by virtue of the ceramic runner 17.
  • the thermal growth of the ceramic is low due to its low coefficient of thermal expansion, thus enabling the runner 17 to more closely track the sealing ring 8 resulting in a more constant radial gap 9 throughout the entire operating envelope of a turbine engine.
  • the ceramic runner 17 could be in rubbing contact with the carbon sealing ring 8, thus either eliminating or reducing the need for cooling of the seal rotor 16.
  • Munson describes a circumferential seal with a ceramic runner for use within a turbine engine.
  • a seal assembly 28 including carbon sealing rings 33 contacting a ceramic seal runner 38.
  • the carbon sealing rings 33 are housed within a stator 30 between a flange 31 attached to the stator 30 at a first end and a removable locking ring 32 at a second end.
  • the stator 30 contacts and is attached to a housing 29 along the engine.
  • the seal runner 38 is a cylinder or sleeve- shaped element residing about a portion of the shaft 40.
  • the shaft 40 is attached to a shaft structure 39 so that the shaft structure 39 and elements secured thereto rotate with the shaft 40.
  • a first end of the shaft 40 includes a flange 41 projecting from the shaft 40 in FIGS.
  • the spool member 45 is further attached to the shaft structure 39.
  • the second end of the shaft 40 includes a locking ring 43 which is attached to the shaft 40 in a removable fashion in FIGS. 3 and 4 or to the spool member 45 in FIG. 5.
  • the seal runner 38 is fixed to the shaft 40, so as to rotate therewith, by applying a compressive force in the direction of the flange 41 when the locking ring 43 is secured to the shaft 40 or spool member 45.
  • a face seal 44 is provided between the seal runner 38 and locking ring 43 to prevent gases from bypassing the seal formed between the inward facing sealing surfaces 34 along the sealing rings 33 and the outward facing sealing surface 35 along the seal runner 38.
  • a washer 42 is also provided between the seal runner 38 and the flange 41 to prevent gases from bypassing the seal formed between the inward facing sealing surfaces 34 and the outward facing sealing surface 35.
  • the face seal 44 is axially compliant so that it is deformed in response to the relative changes in the length between the seal runner 38 and the shaft 40 and shaft structure 39.
  • each resilient member 36 includes a plurality of plates 37 each having deflectable, resilient fingers.
  • each resilient member 36 is a ring with a u-shaped cross section. The resilient members 36 separately form a gas-tight seal within the cavity between the seal runner 38 and the shaft structure 39.
  • each resilient member 36 is a ring with a u-shaped cross section attached to comprise a single structure.
  • a means for attaching a ceramic runner to a rotatable metal shaft that allows the runner to be used in a circumferential seal system and avoids damage to the runner associated with cyclic expansion and contraction of components with a turbine engine.
  • What is also required is a means for attaching a ceramic runner within a circumferential seal system to a rotatable metal shaft that allows for sealing between the runner and shaft while avoiding damage to the sealing surface during use.
  • An object of the invention is to provide a means for attaching a ceramic runner to a rotatable metal shaft that allows the runner to be used in a circumferential seal system and avoids damage to the runner associated with cyclic expansion and contraction of components with a turbine engine.
  • An object of the invention is to provide a means for attaching a ceramic runner within a circumferential seal system to a rotatable metal shaft that allows for sealing between the runner and shaft while avoiding damage to the sealing surface during use.
  • An object of the invention is to provide a means for attaching a ceramic runner within a circumferential seal system which allows for axial movement of the ceramic runner while avoiding the problems of the related arts.
  • An object of the invention is to provide a means for attaching a ceramic runner within a circumferential seal system which avoids radial expansion of the ceramic runner resulting from the radial expansion of a rotatable metal shaft and components thereon.
  • the circumferential seal includes a ceramic runner, an annular seal ring, at least one tolerance ring, and a pair of sealing rings.
  • the ceramic runner is circumscribed about a shaft within a recess along the shaft. The recess is bounded by a shoulder and a clamping ring.
  • a first annular gap is disposed between a first end of the ceramic runner and the shoulder.
  • a second end of the ceramic runner directly contacts the clamping ring.
  • An anti-rotation pin is attached to the clamping ring and extends into a slot along the ceramic runner.
  • At least one non-sealing spring mechanism is disposed between and directly contacts the shoulder and the first end along the first annular gap.
  • the non-sealing spring mechanism applies a biasing force onto the ceramic runner toward the clamping ring.
  • the annular seal ring is circumscribed about the ceramic runner and disposed within a seal housing so that the annular seal ring is stationary.
  • the tolerance ring(s) directly contacts the ceramic runner and the shaft along a second annular gap between the ceramic runner and the shaft.
  • the ceramic runner is fixed to the shaft via the tolerance ring(s), anti-rotation pin, and non-sealing spring mechanism so that the ceramic runner rotates with the shaft.
  • the non-sealing spring mechanism expands and contracts in response to expansion and contraction of the ceramic runner.
  • the pair of sealing rings directly contacts the ceramic runner and the shaft along the second annular gap.
  • the tolerance ring(s) is disposed between the pair of sealing rings.
  • the non-sealing spring mechanism is a wave spring or a compression spring.
  • the non-sealing spring mechanism is compression springs separately disposed about the first annular gap and attached to the shoulder along the shaft.
  • each tolerance ring and each sealing ring is separately disposed within an equal number of annular grooves along the ceramic runner.
  • each tolerance ring and each sealing ring is separately disposed within an equal number of annular grooves along the shaft.
  • the annular seal ring forms a contact seal or a non-contact seal about the ceramic runner.
  • the sealing ring is an O-ring, a spring-energized seal, or a high-temperature metallic seal ring.
  • the circumferential seal includes a ceramic runner, an annular seal ring, at least one tolerance ring, and a pair of sealing rings.
  • the ceramic runner is circumscribed about a recess along a shaft. The recess is bounded by a shoulder and a clamping ring.
  • a first annular gap is disposed between a second end of the ceramic runner and the clamping ring.
  • a first end of the ceramic runner directly contacts the shoulder along the shaft.
  • An anti-rotation pin is attached to the shoulder and extends into a slot along the ceramic runner.
  • At least one non-sealing spring mechanism is disposed between and directly contacts the clamping ring and the second end along the first annular gap.
  • At least one non-sealing spring mechanism applies a biasing force onto the ceramic runner toward the shoulder.
  • the annular seal ring is circumscribed about the ceramic runner and disposed within a seal housing so that the annular seal ring is stationary.
  • the tolerance ring(s) directly contacts the ceramic runner and the shaft along a second annular gap between the ceramic runner and the shaft.
  • the ceramic runner is fixed to the shaft via the tolerance ring(s), anti-rotation pin, and non-sealing spring mechanism so that the ceramic runner rotates with the shaft.
  • the non-sealing spring mechanism expands and contracts in response to expansion and contraction of the ceramic runner.
  • the pair of sealing rings directly contacts the ceramic runner and the shaft along the second annular gap.
  • the tolerance ring(s) is disposed between the pair of sealing rings.
  • the non-sealing spring mechanism is a wave spring or a compression spring.
  • the non-sealing spring mechanism is compression springs separately disposed about the first annular gap and attached to the clamping ring.
  • each tolerance ring and each sealing ring is separately disposed within an equal number of annular grooves along the ceramic runner.
  • each tolerance ring and each sealing ring is separately disposed within an equal number of annular grooves along the shaft.
  • the annular seal ring forms a contact seal or a non-contact seal about the ceramic runner.
  • the sealing ring is an O-ring, a spring-energized seal, or a high-temperature metallic seal ring.
  • the circumferential seal includes a carrier, a ceramic runner, an annular seal ring, at least one tolerance ring, and a pair of sealing rings.
  • the carrier is disposed about and directly contacts a shaft within a recess along the shaft.
  • the carrier is rotatable with the shaft.
  • the carrier has a shoulder at one end.
  • the ceramic runner is circumscribed about the carrier and disposed between the shoulder and a clamping ring.
  • a first annular gap is disposed between a first end of the ceramic runner and the shoulder.
  • a second end of the ceramic runner directly contacts the clamping ring.
  • An anti-rotation key is attached to the clamping ring and extends into a slot along the ceramic runner.
  • At least one non- sealing spring mechanism directly contacts the shoulder and the first end along the first annular gap.
  • the non-sealing spring mechanism applies a biasing force onto the ceramic runner toward the clamping ring.
  • the annular seal ring is circumscribed about the ceramic runner and disposed within a seal housing so that the annular seal ring is stationary.
  • the tolerance ring(s) directly contacts the ceramic runner and the carrier along a second annular gap between the ceramic runner and the carrier.
  • the ceramic runner is fixed to the carrier via the tolerance ring(s), anti-rotation key, and non-sealing spring mechanism so that the ceramic runner rotates with the carrier.
  • the non-sealing spring mechanism expands and contracts in response to expansion and contraction of the ceramic runner.
  • the pair of sealing rings directly contacts the ceramic runner and the carrier along the second annular gap.
  • the tolerance ring(s) is disposed between the pair of sealing rings.
  • the non-sealing spring mechanism is a wave spring or a compression spring.
  • the non-sealing spring mechanism is compression springs separately disposed about the first annular gap and attached to the shoulder.
  • each tolerance ring and each sealing ring is separately disposed within an annular groove along the carrier.
  • each tolerance ring and each sealing ring is separately disposed within an annular groove along the ceramic runner.
  • the annular seal ring forms a contact seal or a non-contact seal about the ceramic runner.
  • the sealing ring is an O-ring, a spring-energized seal, or a high-temperature metallic seal ring.
  • the circumferential seal includes a carrier, a ceramic runner, an annular seal ring, at least one tolerance ring, and a pair of sealing rings.
  • the carrier is disposed about and directly contacts a shaft within a recess along the shaft.
  • the carrier is rotatable with the shaft.
  • the carrier has a shoulder at one end.
  • the ceramic runner is circumscribed about the carrier and disposed between the shoulder and a clamping ring.
  • a first annular gap is disposed between a second end of the ceramic runner and the clamping ring.
  • a first end of the ceramic runner directly contacts the shoulder.
  • An anti-rotation key is attached to the shoulder and extends into a slot along the ceramic runner.
  • At least one non-sealing spring mechanism directly contacts the clamping ring and the second end along the first annular gap.
  • the non-sealing spring mechanism applies a biasing force onto the ceramic runner toward the shoulder.
  • the annular seal ring is circumscribed about the ceramic runner and disposed within a seal housing so that the annular seal ring is stationary.
  • the tolerance ring(s) directly contacts the ceramic runner and the carrier along a second annular gap between the ceramic runner and the carrier.
  • the ceramic runner is fixed to the carrier via the tolerance ring(s), anti-rotation key, and non- sealing spring mechanism so that the ceramic runner rotates with the carrier.
  • the non- sealing spring mechanism expands and contracts in response to expansion and contraction of the ceramic runner.
  • the pair of sealing rings directly contacts the ceramic runner and the carrier along the second annular gap.
  • the tolerance ring(s) is disposed between the pair of sealing rings.
  • the non-sealing spring mechanism is a wave spring or a compression spring.
  • the non-sealing spring mechanism is compression springs separately disposed about the first annular gap and attached to the clamping ring.
  • each tolerance ring and each sealing ring is separately disposed within an annular groove along the carrier.
  • each tolerance ring and each sealing ring is separately disposed within an annular groove along the ceramic runner.
  • the annular seal ring forms a contact seal or a non-contact seal about the ceramic runner.
  • the sealing ring is an O-ring, a spring-energized seal, or a high-temperature metallic seal ring.
  • the circumferential seal includes a carrier, a ceramic runner, an annular seal ring, at least one tolerance ring, and a pair of sealing rings.
  • the carrier is disposed about and directly contacts a shaft within a recess along the shaft.
  • the carrier is rotatable with the shaft.
  • the carrier has a shoulder at one end.
  • the ceramic runner is circumscribed about the carrier and disposed between the shoulder and a clamping ring.
  • a first annular gap is disposed between a first end of the ceramic runner and the shoulder.
  • a second end of the ceramic runner directly contacts the clamping ring.
  • An anti-rotation screw is attached to the carrier and extends into a hole along the ceramic runner.
  • At least one non- sealing spring mechanism directly contacts the shoulder and the first end along the first annular gap.
  • the non-sealing spring mechanism applies a biasing force onto the ceramic runner toward the clamping ring.
  • the annular seal ring is circumscribed about the ceramic runner and disposed within a seal housing so that the annular seal ring is stationary.
  • the tolerance ring(s) directly contacts the ceramic runner and the carrier along a second annular gap between the ceramic runner and the carrier.
  • the ceramic runner is fixed to the carrier via the tolerance ring(s), anti-rotation screw, and non-sealing spring mechanism so that the ceramic runner is rotatable with the carrier.
  • the non-sealing spring mechanism expands and contracts in response to expansion and contraction of the ceramic runner.
  • At least one sealing ring directly contacts the ceramic runner and the carrier along the second annular gap.
  • the tolerance ring(s) and anti-rotation screw are disposed between the pair of sealing rings.
  • the non-sealing spring mechanism is a wave spring or a compression spring.
  • the non-sealing spring mechanism is compression springs separately disposed about the first annular gap and attached to the shoulder.
  • each tolerance ring and one sealing ring is separately disposed within an annular groove along the carrier and another sealing ring is disposed within another annular groove along the clamping ring.
  • each tolerance ring and one sealing ring is separately disposed within an annular groove along the ceramic runner and another sealing ring is disposed within another annular groove along the clamping ring.
  • the annular seal ring forms a contact seal or a non-contact seal about the ceramic runner.
  • the sealing ring is an O-ring, a spring-energized seal, or a high-temperature metallic seal ring.
  • the circumferential seal includes a carrier, a ceramic runner, an annular seal ring, at least one tolerance ring, and a pair of sealing rings.
  • the carrier is disposed about and directly contacts a shaft within a recess along the shaft.
  • the carrier is rotatable with the shaft.
  • the carrier has a shoulder at one end.
  • a ceramic runner is circumscribed about the carrier and disposed between the shoulder and a clamping ring.
  • a first annular gap is disposed between a second end of the ceramic runner and the clamping ring.
  • a first end of the ceramic runner directly contacts the shoulder.
  • An anti-rotation screw is attached to the carrier and extends into a hole along the ceramic runner.
  • At least one non-sealing spring mechanism directly contacts the clamping ring and the second end along the first annular gap.
  • the non-sealing spring mechanism applies a biasing force onto the ceramic runner toward the shoulder.
  • the annular seal ring is circumscribed about the ceramic runner and disposed within a seal housing so that the annular seal ring is stationary.
  • the tolerance ring(s) directly contacts the ceramic runner and the carrier along a second annular gap between the ceramic runner and the carrier.
  • the ceramic runner is fixed to the carrier via the tolerance ring(s), anti -rotation screw, and non- sealing spring mechanism so that the ceramic runner is rotatable with the carrier.
  • the non-sealing spring mechanism expands and contracts in response to expansion and contraction of the ceramic runner.
  • At least one sealing ring directly contacts the ceramic runner and the carrier along the second annular gap.
  • the tolerance ring(s) and anti-rotation screw are disposed between the pair of sealing rings.
  • the non-sealing spring mechanism is a wave spring or a compression spring.
  • the non-sealing spring mechanism is compression springs separately disposed about the first annular gap and attached to the clamping ring.
  • each tolerance ring and one sealing ring is separately disposed within an annular groove along the carrier and another sealing ring is disposed within another annular groove along the clamping ring.
  • each tolerance ring and one sealing ring is separately disposed within an annular groove along the ceramic runner and another sealing ring is disposed within another annular groove along the clamping ring.
  • the annular seal ring forms a contact seal or a non-contact seal about the ceramic runner.
  • the sealing ring is an O-ring, a spring-energized seal, or a high-temperature metallic seal ring.
  • the shaft rotates with respect to the annular seal ring.
  • the ceramic runner is configured to rotate with the shaft via the non-sealing spring mechanism, anti-rotation element, and tolerance ring(s).
  • the non- sealing spring mechanism applies an axial load onto the ceramic runner biasing the runner against the clamping ring attached to the shaft. Friction between the ceramic runner and clamping ring resists relative rotational motion between the runner and shaft. Relative motion is further avoided by the anti-rotation element fixed to and movable with the shaft.
  • the anti-rotation element contacts the ceramic runner thereby arresting rotation between runner and shaft. Contact by the tolerance rings between the ceramic runner and shaft or a carrier along the shaft further resists relative rotational motion between the runner and shaft.
  • the invention utilizes a spring mechanism which deflects or compresses axially along the length of the shaft to accommodate thermal expansion axially along the ceramic runner during operation of the turbine engine so as to minimize stresses within the ceramic runner thereby minimizing the possibility of stress induced failures.
  • the invention utilizes a spring mechanism which allows the ceramic runner to expand independently relative to the shaft and/or carrier so as to minimize stresses within the ceramic runner thereby minimizing the possibility of stress induced failures.
  • the invention utilizes sealing rings between the ceramic runner and shaft or a carrier along the shaft which prevent oil leakage under the ceramic runner thereby minimizing oil coking under the runner.
  • the invention utilizes sealing rings between the ceramic runner and shaft or a carrier along the shaft about the tolerance ring which prevent oil from contacting the tolerance ring(s) thereby avoiding slippage between the runner and shaft or carrier.
  • the invention utilizes one or more sealing rings between the ceramic runner and shaft or a carrier along the shaft to radially deflect and accommodate changes in the clearance between the runner and shaft or carrier as the shaft and/or carrier expands thereby avoiding radial expansion by and damage to the runner.
  • the invention utilizes one or more gapped tolerance rings between the ceramic runner and shaft or carrier which expands circumferentially so as to accommodate changes in the clearance between the runner and shaft or carrier as the shaft and/or carrier expands thereby avoiding radial expansion by and damage to the runner.
  • the invention separates axial functionality of the spring mechanism from sealing function of the sealing rings thereby minimizing degradation of the sealing rings by thermally induced expansion and contraction cycles within a gas turbine engine.
  • the invention separates radial functionality of the tolerance ring(s) from sealing function of the sealing rings thereby minimizing degradation of the sealing rings by thermally induced expansion and contraction cycles within a gas turbine engine.
  • FIG. 1 is a cross-sectional view illustrating a circumferential seal with metal rotor as described by Ullah et al. in United States Patent No. 6,322,081 ;
  • FIG. 2 is a cross-sectional view illustrating a circumferential seal with ceramic rotor as described by Ullah et al. in United States Patent No. 6,322,081 ;
  • FIG. 3 is a cross-section view illustrating a circumferential seal with a ceramic runner attached compressively along a shaft between a flange and a locking ring and radially supported along the shaft via a pair of resilient members each having a plurality of plates as described by Munson in United States Patent No. 7,905,395;
  • FIG. 4 is a cross-section view illustrating a circumferential seal with a ceramic runner attached compressively along a shaft between a flange and a locking ring and radially supported along the shaft via a pair of resilient members each being a ring with u-shaped cross section as described by Munson in United States Patent No. 7,905,395;
  • FIG. 5 is a cross-section view illustrating a circumferential seal with a ceramic runner attached compressively along a spool member between a flange and a locking ring and radially supported along the spool member via a pair of resilient members each being a ring with u-shaped cross section which form a single structure as described by Munson in United States Patent No. 7,905,395;
  • FIG. 6a is a cross-section view illustrating a circumferential seal with a ceramic runner recessed along a rotatable shaft and attached thereto via at least one anti-rotation pin and an annular spring wherein sealing and tolerance rings are disposed between the runner and shaft within annular grooves along the runner in accordance with an embodiment of the invention;
  • FIG. 6b is a cross-section view illustrating the anti -rotation pin in FIG. 6a within a slot or hole along the ceramic runner in accordance with an embodiment of the invention
  • FIG. 6c is a side view illustrating the tolerance ring in FIG. 6a with a gap in accordance with an embodiment of the invention
  • FIG. 6d is a cross-section view illustrating a circumferential seal with a ceramic runner recessed along a rotatable shaft and attached thereto via at least one anti-rotation pin and an annular spring wherein the spring mechanism is provided between the ceramic runner and a clamping ring in accordance with an embodiment of the invention
  • FIG. 7a is a cross-section view illustrating a circumferential seal with a ceramic runner recessed along a rotatable shaft and attached thereto via at least one anti-rotation pin and an annular spring wherein sealing and tolerance rings are disposed between the runner and shaft within annular grooves along the shaft in accordance with an embodiment of the invention
  • FIG. 7b is a cross section view illustrating a compression spring disposed between the ceramic runner and shaft in FIG. 7a in accordance with an embodiment of the invention
  • FIG. 7c is a cross-section view illustrating several compression springs each within a hole along a portion of the shaft in accordance with an embodiment of the invention
  • FIG. 8a is a cross-section view illustrating a circumferential seal with a ceramic runner disposed along a carrier recessed along a rotatable shaft and attached to the carrier via at least one key and a plurality of compression springs wherein sealing and tolerance rings are disposed between the runner and shaft within annular grooves along the carrier in accordance with an embodiment of the invention
  • FIG. 8b is a cross-section view illustrating the key in FIG. 8a within a slot along the ceramic runner in accordance with an embodiment of the invention
  • FIG. 8c is a cross-section view illustrating several compression springs each within a hole along a portion of the carrier in accordance with an embodiment of the invention.
  • FIG. 8d is a cross section view illustrating an annular spring disposed between the ceramic runner and carrier in FIG. 8a in accordance with an embodiment of the invention
  • FIG. 8e is a cross-section view illustrating a circumferential seal with a ceramic runner disposed along a carrier recessed along a rotatable shaft wherein the spring mechanism is disposed between the ceramic runner and a clamping ring in accordance with an embodiment of the invention
  • FIG. 9a is a cross-section view illustrating a circumferential seal with a ceramic runner disposed along a carrier recessed along a rotatable shaft and attached to the carrier via at least one anti-rotation screw and a plurality of compression springs wherein a first sealing ring and tolerance ring are disposed between the runner and shaft within annular grooves along the shaft and a second sealing ring is disposed between the runner and a clamping ring along a groove within the clamping ring in accordance with an embodiment of the invention;
  • FIG. 9b is a cross-section view illustrating the anti-rotation screw in FIG. 9a disposed within a hole along the carrier in accordance with an embodiment of the invention
  • FIG. 9c is a cross-section view illustrating the anti-rotation screw in FIG. 9a disposed within a hole along the ceramic runner in accordance with an embodiment of the invention.
  • FIG. 9d is a cross-section view illustrating a circumferential seal with a ceramic runner disposed along a carrier recessed along a rotatable shaft and attached to the carrier via at least one anti -rotation screw and a plurality of compression springs wherein a first sealing ring and tolerance ring are disposed between the runner and shaft within annular grooves along the shaft and a second sealing ring is disposed between the runner and the carrier along a groove within the carrier in accordance with an embodiment of the invention.
  • FIG. 9e is a cross-section view illustrating a circumferential seal with a ceramic runner disposed along a carrier recessed along a rotatable shaft wherein a spring mechanism is disposed between the ceramic runner and a clamping ring in accordance with an embodiment of the invention.
  • the circumferential seal 46 is illustrated for descriptive purposes along an upper half of an exemplary shaft 57 rotatable about a centerline 67 along a turbine engine. While the shaft 57 is generally represented as a cylindrical-shaped element, other configurations are possible.
  • the outer diameter 100 of the shaft 57 is shown including a recess 98.
  • the recess 98 could include one or more regions along the shaft 57 each having a diameter smaller than the outer diameter 100 of the shaft 57.
  • the exemplary shafts 57 in FIGS. 6a and 7a have a recess 98 which includes three sections arranged end-to-end in a stepwise fashion, whereby the first section accommodates a ceramic runner 52, the second section accommodates a clamping ring 74, and the third section
  • the clamping ring 74 and locking ring 75 are composed of materials suitable for use within a turbine engine. Materials should be wear, failure, and temperature resistant. Exemplary compositions include metals, preferably compositions of steel.
  • the locking ring 75 secures the various components described herein to the shaft 57 about the recess 98. It is understood that the recess 98 could include one or more sections as well as other shapes and designs which facilitate attachment of elements required to provide circumferential sealing along a shaft 57.
  • the interface between the outer diameter 100 of the shaft 57 and the outer diameter 62 of the recess 98 is defined by a first shoulder 55.
  • the recess 98 could include additional shoulders depending on the profile of the recess 98, although such features are optional and design dependent.
  • the recess 98 in FIGS. 6a and 7a is shown with a second shoulder 56 at the interface between the regions for the ceramic runner 52 and clamping ring 74 formed at the discontinuity of the outer diameters 62, 79.
  • the second shoulder 56 acts as a mechanical stop which fixes the clamping ring 74 at a prescribed distance from the first shoulder 55.
  • a clearance fit could be provided between the outer diameter 79 of the shaft 57 and inner diameter 83 along the clamping ring 74 so that the clamping ring 74 is slidable with respect to the shaft 57.
  • the clamping ring 74 is secured to the shaft 57 via the locking ring 75 which could include threads along its inner diameter 84 which engage a complementary thread arrangement along the outer diameter 80 of the shaft 57.
  • the recess 98 at the interface between the regions for the clamping ring 74 and locking ring 75 is shown without a shoulder because these regions include outer diameters 79, 80 which are approximately equal.
  • the ceramic runner 52 is a cylindrically-shaped or sleeve-shaped element which is slid onto the shaft 57 during assembly so as to circumscribe the shaft 57 about the recess 98.
  • the ceramic runner 52 is composed of a ceramic composition suitable for use within a turbine engine. In preferred embodiments, the ceramic composition should be wear, failure, and temperature resistant. Exemplary, non- limiting compositions include silicon nitride and silicon carbide.
  • the ceramic runner 52 has an inner diameter 61 which is larger than the outer diameter 62 of the shaft 57 along the recess 98 resulting in a second annular gap 72 which avoids direct contact between the ceramic runner 52 and shaft 57.
  • the distance between a first end 53 and a second end 54 of the ceramic runner 52 is less than the axial distance between the first shoulder 55 and second shoulder 56.
  • the first end 53 is positioned adjacent to the first shoulder 55 so that a first annular gap 73 separates the first end 53 from the first shoulder 55.
  • the axial length of the first annular gap 73 is sized to accommodate a spring mechanism.
  • the spring mechanism provides no sealing functionality. Although spring mechanisms are described herein, it is understood that such mechanisms could include other non-sealing devices which at least resist compression and are resilient.
  • the second end 54 directly contacts the clamping ring 74 so that the second end 54 is generally aligned with the second shoulder 56.
  • the spring mechanism could be a single annular spring 58, as represented in FIGS. 6a and 7a.
  • Exemplary annular springs 58 include a wave spring or a compression spring or the like which circumscribe the shaft 57 within the first annular gap 73.
  • the length of the annular spring 58 in its uncompressed state requires the annular spring 58 to be partially compressed when assembled between the ceramic runner 52 and shaft 57.
  • the annular spring 58 is compressed by contact with the first shoulder 55 at one end of the annular spring 58 and the first end 53 at another end of the annular spring 58.
  • the annular spring 58 communicates a biasing force 99 axially onto the ceramic runner 52 thereby pressing the ceramic runner 52 onto the clamping ring 74.
  • the biasing force 99 is preferred to maintain contact between the second end 54 of the ceramic runner 52 and the clamping ring 74 during operation of a turbine engine, thereby avoiding axial separation between the ceramic runner 52 and clamping ring 74 which could occur because of thermally induced expansion and contraction of components within the engine.
  • the biasing force 99 also resists rotational sliding motion between the ceramic runner 52 and clamping ring 74 at the second end 54.
  • the annular spring 58 is partially compressed at or below ambient conditions so as to allow for further compression of the annular spring 58 during operation of a turbine engine. This feature allows the annular spring 58 to expand and contract with axial expansion and contraction of the ceramic runner 52 as the ceramic runner 52 and other components heat and cool.
  • the spring mechanism could include a plurality of compression springs 88 or the like, as represented in FIGS. 7b and 7c.
  • Each compression spring 88 is axially aligned along the direction of the shaft 57 as shown in FIG. 7b.
  • the compression springs 88 are further separately disposed about the diameter of the shaft 57 along the first shoulder 55 as generally shown in FIG. 7c, so as to communicate a biasing force 99 symmetrically about the ceramic runner 52 in the axial direction.
  • One end of each compression spring 88 could reside within a complementary shaped hole 94 so that a portion of the compression spring 88 extends into the first annular gap 73 with sufficient length to contact the first end 53 along the ceramic runner 52.
  • the compression spring 88 could be mechanically fixed to the hole 94 via an interference fit or freely movable within the hole 94.
  • the compression springs 88 are preferred to be sufficiently long so that each is partially compressed when assembled between the shaft 57 and ceramic runner 52. Partial compression of the compression spring 88 maintains a biasing force 99 onto the ceramic runner 52 so that the second end 54 of the ceramic runner 52 is biased toward and contacts the clamping ring 74.
  • the biasing force 99 maintains contact between the second end 54 of the ceramic runner 52 and the clamping ring 74 during operation of a turbine engine, thereby avoiding axial separation thereof because of thermally induced expansion and contraction of ceramic runner 52 and other components within the engine.
  • the biasing force 99 also resists rotational sliding motion between the ceramic runner 52 and clamping ring 74 at the second end 54.
  • the compression springs 88 are partially compressed at or below ambient conditions so as to allow for further compression of the compression springs 88 during operation of a turbine engine. This feature allows the compression springs 88 to expand and contract with expansion and contraction of the ceramic runner 52 as the ceramic runner 52 and other components heat and cool.
  • the first end 53 could directly contact the first shoulder 55 and the spring mechanism, either the annular spring 58 or the compression springs 88, is disposed between the second end 54 and clamping ring 74, as generally represented in FIG. 6d.
  • the first annular gap 73 now resides between the second end 54 and clamping ring 74.
  • the biasing force 99 is directed toward the shoulder 55.
  • the anti-rotation pin 76 partially resides within a hole 77 and is attached to the shaft 57 along the first shoulder 55 so as to extend toward the ceramic runner 52. Another portion of the anti -rotation pin 76 resides within a slot 78 along the first side 53.
  • the spring mechanisms could be attached to the clamping ring 74 in a similar manner as otherwise described herein for attachment to the shaft 57.
  • the second annular gap 72 between the inner diameter 61 of the ceramic runner 52 and outer diameter 62 of the shaft 57 is shown with a pair of tolerance rings 70, 71.
  • the tolerance rings 70, 71 are generally described as a ring- shaped element with corrugations along an inward face or an outward face and with a gap 87, the latter feature represented in FIG. 6c (corrugated structure not shown). Tolerance rings 70, 71 provide no sealing functionality.
  • the tolerance rings 70, 71 When attached between the inner diameter 61 and outer diameter 62 along the gap 72, the tolerance rings 70, 71 conform to the bore and are self-retaining thereby resisting rotational slippage between the ceramic runner 52 and shaft 57.
  • the tolerance rings 70, 71 could allow for axial slippage so as to avoid stresses within the ceramic runner 52.
  • Exemplary tolerance rings 70, 71 are the BN Series devices sold by USA Tolerance Rings of Pennington, New Jersey (United States).
  • the tolerance rings 70, 71 maintain proper fit between the ceramic runner 52 and shaft 57 by expanding circumferentially to the radial clearance between the inner diameter 61 and outer diameter 62 by closing the gap 87. This functionality avoids radial expansion of the ceramic runner 52 which could damage the runner 52.
  • Each tolerance ring 70, 71 resides within an annular groove 63, 65, respectively.
  • the annular grooves 63, 65 are disposed along the inner diameter 61 of the ceramic runner 52 as shown in FIG. 6a or along the outer diameter 52 of the shaft 57 as shown in FIG. 7a.
  • the depth of each annular groove 63, 65 should allow assembly of the ceramic runner 52 onto the shaft 57 and proper placement of the tolerance rings 70, 71 along the shaft 57 while ensuring sufficient contact between the tolerance rings 70, 71 and inner and outer diameters 61 , 62 for proper function of the tolerance rings 70, 71.
  • the annular grooves 63, 65 should be at least as wide as the tolerance rings 70, 71, preferably providing a tolerance fit which allows each tolerance ring 70, 71 to be secured within the respective annular groove 63, 65.
  • sealing rings 68, 69 could include devices known within the art, examples including, but not limited to, multi-directional O- rings, unidirectional spring-energized seals, high-temperature metallic seal rings, or other comparable devices sold by the Parker Hannifin Corporation located in North Haven, Connecticut (United States) or other suppliers.
  • Other exemplary seals include those sold under the Trademark OMNISEAL ® by Saint-Gobain Performance Plastics Corporation of Aurora, Ohio (United States).
  • each sealing ring 68, 69 resides within an annular groove 64, 66, respectively.
  • the annular grooves 64, 66 are disposed along the inner diameter 61 of the ceramic runner 52 as shown in FIG. 6a or along the outer diameter 52 of the shaft 57 as shown in FIG. 7a.
  • each annular groove 64, 66 should be sufficiently deep so as to allow assembly of the ceramic runner 52 onto the shaft 57 and proper placement of the sealing rings 68, 69 along the shaft 57 while ensuring sufficient contact between the sealing rings 68, 69 and inner and outer diameters 61, 62 for proper function of the sealing rings 68, 69.
  • the grooves 64, 66 should be at least as wide as the sealing rings 68, 69, preferably with a tolerance fit allowing each sealing ring 68, 69 to be secured within the respective annular groove 64, 66.
  • the sealing rings 68, 69 are disposed about the tolerance rings 70, 71, as represented in FIGS. 6a and 7a.
  • the sealing rings 68, 69 are oriented along the second annular gap 72 so that the sealing direction 101 of the sealing rings 68, 69 avoids or at least minimizes oil and other contaminants within the higher and/or lower pressure sides 81, 82 from entering the second annular gap 72 and interacting with the tolerance rings 70, 71. This feature minimizes degradation to the performance of the tolerance rings 70, 71 caused by oil and other contaminants and further minimizes oil coking under the ceramic runner 52.
  • the clamping ring 74 further includes at least one anti-rotation pin 76.
  • the anti-rotation pin 76 could reside within a complementary shaped hole 77 along the clamping ring 74 so that a portion of the anti -rotation pin 76 extends toward the ceramic runner 52.
  • the anti-rotation pin 76 could be mechanically fixed to the hole 77 via an interference fit or slidable therein via a clearance fit.
  • the portion of the anti- rotation pin 76 extending from the clamping ring 74 could reside within a slot 78 along the ceramic runner 52.
  • the slot 78 could extend from the inner diameter 61 of the ceramic runner 52 and partially traverse the thickness of the ceramic runner 52 in the direction of the outward facing sealing surface 60, as represented in FIG. 6b.
  • the slot 78 is dimensioned to avoid contact with the end and sides of the anti-rotation pin 76, see FIGS. 6a and 6b, respectively.
  • the anti-rotation pin 76 could contact a side wall 102, the latter shown in FIG. 6b, along the slot 78 when the ceramic runner 52 rotates relative to the clamping ring 74.
  • the degree of rotation before contact between the anti -rotation pin 76 and side wall 102 is determined by the clearance
  • An annular seal ring 49 is circumferentially disposed about the outward facing sealing surface 60 of the ceramic runner 52.
  • the annular seal ring 49 includes an inward facing sealing surface 59 which interacts with the outward facing sealing surface 60 to form the circumferential sealing of the present invention.
  • the annular seal ring 49 is a ring-shaped element with or without segmentation.
  • the inward facing sealing surface 59 could physically contact the outward facing sealing surface 60 during rotation of the ceramic runner 52 and shaft 57 to provide a contact seal.
  • the inward facing sealing surface 59 and outward facing sealing surface 60 could be separated by a gap to form a non- contact seal.
  • the outward facing sealing surface 60 could include hydrodynamic pockets which form a thin- film between inward and outward facing sealing surfaces 59, 60 during rotation of the ceramic runner 52.
  • the annular seal ring 49 resides within a seal housing 47 and is secured thereto via a support ring 50 and a retaining ring 51 or other like elements via methods and designs known within the art.
  • the annular seal ring 49 is stationary rotationally with respect to the seal housing 47. As such, the annular seal ring 49 does not rotate with respect to the seal housing 47.
  • the annular seal ring 49 could move radially inward and outward to track radial excursions of the ceramic runner 52.
  • the seal housing 47 is secured to a housing 48 comprising a turbine engine. Both seal housing 47 and housing 48 are shown in a generalized form for descriptive purposes only and are not intended to limit the scope of the claimed invention.
  • Arrangement of the annular seal ring 49, seal housing 47, and housing 48 about the ceramic runner 52 and shaft 57 generally defines a higher pressure side 81 and a lower pressure side 82.
  • the higher pressure side 81 could define the air or gas side within a turbine engine.
  • the lower pressure side 82 could define the bearing or oil side within a turbine engine.
  • outward facing sealing surface 60 along the ceramic runner 52 is shown approximately radially aligned with the outer diameter 100 of the shaft 57.
  • outward facing sealing surface 60 could extend above or be depressed below the outer diameter 100 in other embodiments of the invention.
  • the circumferential seal 46 is illustrated for descriptive purposes along an upper half of an exemplary shaft 57 along a turbine engine rotatable about a centerline 67.
  • a ceramic runner 52 is attached to a carrier 91 to form a cartridge 90.
  • the cartridge 90 facilitates assembly of components comprising the circumferential seal 46 prior to attachment to a shaft 57. This approach simplifies assembly and repair of a turbine engine.
  • the outer diameter 100 of the shaft 57 is shown including a recess 98.
  • the recess 98 could include one or more regions along the shaft 57 each having a diameter smaller than the outer diameter 100.
  • the exemplary shaft 57 has a recess 98 which includes a single section to accommodate a locking ring 75 and a carrier 91 , the latter supporting a ceramic runner 52 and a clamping ring 74.
  • the clamping ring 74 and locking ring 75 are composed of materials suitable for use within a turbine engine. Materials should be wear, failure, and temperature resistant. Exemplary compositions include metals, preferably compositions of steel.
  • the locking ring 75 secures the carrier 91 with the various components described herein to the shaft 57 about the recess 98. It is understood that the recess 98 could include one or more sections as well as other shapes and designs which facilitate attachment of elements required to provide circumferential sealing along a shaft 57.
  • the interface between the outer diameter 100 of the shaft 57 and the outer diameter 62 of the recess 98 defines a first shoulder 55.
  • the recess 98 could include additional shoulders depending on the profile of the recess 98, although such features are optional and design dependent.
  • the recess 98 could include other shoulders each defined by a discontinuity where two outer diameters differ.
  • the carrier 91 is a ring-shaped element with a flange 104 which extends perpendicular from one end of an annular ring 105.
  • a clearance fit is provided for assembly purposes between the outer diameter 62 of the shaft 57 and inner diameter 85 of the carrier 91 so that the carrier 91 is slidable with respect to the shaft 57.
  • an interference fit is provided between the outer diameter 62 and the inner diameter 85 and the carrier 91 is heated to open the inner diameter 85 prior to sliding the carrier 91 onto the shaft 57.
  • the carrier 91 is then cooled to fix the carrier 91 to the shaft 57.
  • the flange 104 should contact the shoulder 55 in addition to the annular ring 105 contacting the surface of the shaft 57.
  • the carrier 91 is composed of materials suitable for use within a turbine engine. Materials should be wear, failure, and temperature resistant. Exemplary compositions include metals, preferably compositions of steel with a coefficient of thermal expansion comparable to that of the shaft 57 so that carrier 91 tracks the expansion and contraction of the shaft 57.
  • the carrier 91 could likewise include one or more shoulders along the surface of the annular ring 105.
  • the interface between the annular surface 107 along the carrier 91 and the outer diameter 106 of the carrier 91 defines a first shoulder 92.
  • the carrier 91 could also include a first segment with an outer diameter 106 and a second segment with an outer diameter 86.
  • the outer diameter 106 could be larger than the other outer diameter 86 so that a second shoulder 103 is provided at the discontinuity between the two outer surfaces.
  • a clearance fit could be provided between the outer diameter 86 of the carrier 91 and inner diameter 83 along the clamping ring 74 so that the clamping ring 74 is slidable with respect to the carrier 91.
  • the carrier 91 and clamping ring 74 are secured to the shaft 57 via the locking ring 75.
  • the locking ring 75 contacts both the clamping ring 74 and the end 93 of the carrier 91 as illustrate in FIG. 8a.
  • the locking ring 75 includes threads along its inner diameter 84 which engage a complementary thread arrangement along the outer diameter 80 of the shaft 57. The force applied by the locking ring 75 onto the carrier 91 and clamping ring 74 should be sufficient to prevent relative motion with respect to the shaft 57.
  • the ceramic runner 52 is a cylindrically-shaped or sleeve-shaped element which is slid onto the shaft 57 during assembly so as to circumscribe the carrier 91.
  • the ceramic runner 52 is composed of a ceramic composition suitable for use within a turbine engine. In preferred embodiments, the ceramic composition should be wear, failure, and temperature resistant. Exemplary, non-limiting compositions include silicon nitride and silicon carbide.
  • the ceramic runner 52 has an inner diameter 61 which is larger than the outer diameter 106 of the carrier 91 resulting in a second annular gap 72 which avoids direct contact between the ceramic runner 52 and carrier 91.
  • the distance between a first end 53 and a second end 54 of the ceramic runner 52 is less than the axial distance between the first shoulder 92 and second shoulder 103.
  • the first end 53 is positioned adjacent to the first shoulder 92 so that a first annular gap 73 separates the first end 53 from the first shoulder 92.
  • the axial length of the first annular gap 73 is sized to accommodate a spring mechanism.
  • the spring mechanism provides no sealing functionality. Although spring mechanisms are described herein, it is understood that such mechanisms could include other non-sealing devices which at least resist compression and are resilient.
  • the second end 54 directly contacts the clamping ring 74 so that the second end 54 is generally aligned with the second shoulder 103.
  • the spring mechanism could include a plurality of compression springs 88 as represented in FIG. 8a and generally described in FIGS. 7b and 7c.
  • Each compression spring 88 is axially aligned along the direction of the shaft 57.
  • the compression springs 88 are further separately disposed about the shaft 57 along the flange 104 of the carrier 91, as generally shown in FIG. 8c, so as to communicate a biasing force 99 symmetrically about the ceramic runner 52 in the axial direction.
  • One end of each compression spring 88 could reside within a complementary shaped hole 94 within the flange 104 so that a portion of the compression spring 88 extends into the first annular gap 73 with sufficient length to contact the first end 53 along the ceramic runner 52.
  • the compression spring 88 could be mechanically fixed to the hole 94 via an interference fit or freely movable within the hole 94.
  • the compression springs 88 are preferred to be sufficiently long so that each is partially compressed when assembled between the carrier 91 and ceramic runner 52. Partial compression of the compression spring 88 maintains a biasing force 99 onto the ceramic runner 52 so that the second end 54 of the ceramic runner 52 is biased toward and contacts the clamping ring 74.
  • the biasing force 99 maintains contact between the second end 54 of the ceramic runner 52 and the clamping ring 74 during operation of a turbine engine, thereby avoiding separation thereof because of thermally induced expansion and contraction of ceramic runner 52 and other components within the engine.
  • the biasing force 99 also resists rotational sliding motion between the ceramic runner 52 and clamping ring 74 at the second end 54.
  • the compression springs 88 are partially compressed at or below ambient conditions so as to allow for further compression of the compression springs 88 during operation of a turbine engine. This feature allows the compression springs 88 to expand and contract with expansion and contraction of the ceramic runner 52 as the ceramic runner 52 and other components heat and cool.
  • the spring mechanism could be a single annular spring 58, as represented in FIG. 8d.
  • Exemplary annular springs 58 include a wave spring or a compression spring or the like which circumscribe the shaft 57 within the first annular gap 73 between the first end 53 of the ceramic runner 52 and first shoulder 92 along the carrier 91.
  • the length of the annular spring 58 in its uncompressed state requires the annular spring 58 to be partially compressed when assembled between the ceramic runner 52 and carrier 91.
  • the annular spring 58 is compressed by contact with the first shoulder 92 at one side of the annular spring 58 and the first end 53 at another side of the annular spring 58.
  • the annular spring 58 communicates a biasing force 99 axially onto the ceramic runner 52 thereby pressing the ceramic runner 52 onto the clamping ring 74.
  • the biasing force 99 is preferred to maintain contact between the second end 54 of the ceramic runner 52 and the clamping ring 74 during operation of a turbine engine, thereby avoiding separation between the ceramic runner 52 and clamping ring 74 which could occur because of thermally induced expansion and contraction of components within the engine.
  • the biasing force 99 also resists rotational sliding motion between the ceramic runner 52 and the clamping ring 74 at the second end 54.
  • the annular spring 58 is partially compressed at or below ambient conditions so as to allow for further compression of the annular spring 58 during operation of a turbine engine. This feature allows the annular spring 58 to expand and contract with axial expansion and contraction of the ceramic runner 52 as the ceramic runner 52 and other components heat and cool.
  • the first end 53 could directly contact the first shoulder 92 and the spring mechanism, either an annular spring 58 or compression springs 88, is disposed between the second end 54 and clamping ring 74, as generally represented in FIG. 8e.
  • the biasing force 99 is directed toward the flange 104.
  • the anti-rotation key 89 is attached to the flange 104 along the carrier 91 so as to extend toward the ceramic runner 52. A portion of the anti-rotation key 89 resides within a slot 78 along the first side 53.
  • the spring mechanisms could be attached to the clamping ring 74 as described in FIG. 8a.
  • each compression spring 88 could partially reside within a hole 94 so as to extend across the first annular gap 73 and contact the second end 54.
  • the second annular gap 72 between the inner diameter 61 of the ceramic runner 52 and outer diameter 106 of the carrier 91 is shown with a pair of tolerance rings 70, 71.
  • the tolerance rings 70, 71 are generally described as a ring- shaped element with corrugations along an inward face or an outward face and with a gap 87, the latter feature represented in FIG. 6c. Tolerance rings 70, 71 provide no sealing functionality.
  • the tolerance rings 70, 71 When attached between the inner diameter 61 and outer diameter 106 along the gap 72, the tolerance rings 70, 71 conform to the bore and are self-retaining thereby resisting rotational slippage between the ceramic runner 52 and carrier 91.
  • the tolerance rings 70, 71 could allow for axial slippage so as to avoid stresses within the ceramic runner 52.
  • Exemplary tolerance rings 70, 71 are the BN Series devices sold by USA Tolerance Rings of Pennington, New Jersey (United States).
  • the tolerance rings 70, 71 maintain proper fit between the ceramic runner 52 and carrier 91 by expanding circumferentially to the radial clearance between the inner diameter 61 and outer diameter 106 by closing the gap 87. This functionality avoids radial expansion of the ceramic runner 52 which could damage the runner 52.
  • Each tolerance ring 70, 71 resides within an annular groove 63, 65, respectively.
  • the annular grooves 63, 65 could be disposed along the inner diameter 61 of the ceramic runner 52 in an arrangement similar to that shown in FIG. 6a or along the outer diameter 106 of the carrier 91 as shown in FIG. 8a.
  • the depth of each annular groove 63, 65 should allow assembly of the ceramic runner 52 onto the carrier 91 and proper placement of the tolerance rings 70, 71 along the carrier 91 while ensuring sufficient contact between the tolerance rings 70, 71 and inner and outer diameters 61, 106 for proper function of the tolerance rings 70, 71.
  • the annular grooves 63, 65 should be at least as wide as the tolerance rings 70, 71, preferably providing a tolerance fit which allows each tolerance ring 70, 71 to be secured within the respective annular groove 63, 65.
  • sealing rings 68, 69 could include devices known within the art, examples including, but not limited to, multi-directional O- rings, unidirectional spring-energized seals, high-temperature metallic seal rings, or other comparable devices sold by the Parker Hannifin Corporation located in North Haven, Connecticut (United States) or other suppliers.
  • Other exemplary seals include those sold under the Trademark OMNISEAL ® by Saint-Gobain Performance Plastics Corporation of Aurora, Ohio (United States).
  • each sealing ring 68, 69 resides within an annular groove 64, 66, respectively.
  • the annular grooves 64, 66 are disposed along the inner diameter 61 of the ceramic runner 52 in an arrangement similar to that shown in FIG. 6a or along the outer diameter 106 of the carrier 91 as shown in FIG. 8a.
  • each annular groove 64, 66 should be sufficiently deep so as to allow assembly of the ceramic runner 52 onto the carrier 91 and proper placement of the sealing rings 68, 69 along the carrier 91 while ensuring sufficient contact between the sealing rings 68, 69 and inner and outer diameters 61, 106 for proper function of the sealing rings 68, 69.
  • the grooves 64, 66 should be at least as wide as the sealing rings 68, 69, preferably with a tolerance fit allowing each sealing ring 68, 69 to be secured within the respective annular groove 64, 66.
  • the sealing rings 68, 69 are disposed about the tolerance rings 70, 71, as represented in FIG. 8a.
  • the sealing rings 68, 69 are oriented along the second annular gap 72 so that the sealing direction 101 of the sealing rings 68, 69 avoids or at least minimizes oil and other contaminants within the higher and/or lower pressure sides 81, 82 from entering the second annular gap 72 and interacting with the tolerance rings 70, 71. This feature minimizes degradation to the performance of the tolerance rings 70, 71 caused by oil and other contaminants and further minimizes oil coking under the ceramic runner 52.
  • the clamping ring 74 further includes at least one anti-rotation key 89.
  • the anti-rotation key 89 is attached or fixed to one side of the clamping ring 74 via techniques understood in the art so that a portion of the anti-rotation key 89 extends toward the ceramic runner 52.
  • the portion of the anti-rotation key 89 extending from the clamping ring 74 could reside within a slot 78 along the ceramic runner 52.
  • the slot 78 could extend from the inner diameter 61 of the ceramic runner 52 and partially traverse the thickness of the ceramic runner 52 in the direction of the outward facing sealing surface 60, as represented in FIG. 8b.
  • the anti-rotation key 89 could include a circular head as shown in FIG. 8b or a substantially rectangular head.
  • the slot 78 is dimensioned to avoid contact with the end and sides of the anti-rotation key 89, see FIGS. 8a and 8b, respectively.
  • the anti-rotation key 89 could contact a side wall 102, the latter shown in FIG. 8b, along the slot 78 when the ceramic runner 52 rotates relative to the clamping ring 74.
  • the degree of rotation before contact between the anti-rotation key 89 and side wall 102 is determined by the clearance therebetween, which is design dependent.
  • An annular seal ring 49 is circumferentially disposed about the outward facing sealing surface 60 of the ceramic runner 52.
  • the annular seal ring 49 includes an inward facing sealing surface 59 which interacts with the outward facing sealing surface 60 to form the circumferential sealing of the present invention.
  • the annular seal ring 49 is a ring-shaped element with or without segmentation.
  • the inward facing sealing surface 59 could physically contact the outward facing sealing surface 60 during rotation of the ceramic runner 52 and shaft 57 to provide a contact seal.
  • the inward facing sealing surface 59 and outward facing sealing surface 60 could be separated by a gap to form a non- contact seal.
  • the outward facing sealing surface 60 could include hydrodynamic pockets which form a thin- film between inward and outward facing sealing surfaces 59, 60 during rotation of the ceramic runner 52.
  • the annular seal ring 49 resides within a seal housing 47 and is secured thereto via a support ring 50 and a retaining ring 51 or other like elements via methods and designs known within the art.
  • the annular seal ring 49 is rotationally stationary with respect to the seal housing 47. As such, the annular seal ring 49 does not rotate with respect to the seal housing 47.
  • the annular seal ring 49 could move radially inward and outward to track radial excursions of the ceramic runner 52.
  • the seal housing 47 is secured to a housing 48 comprising a turbine engine. Both seal housing 47 and housing 48 are shown in a generalized form for descriptive purposes only and are not intended to limit the scope of the claimed invention.
  • Arrangement of the annular seal ring 49, seal housing 47, and housing 48 about the ceramic runner 52 and shaft 57 generally defines a higher pressure side 81 and a lower pressure side 82.
  • the higher pressure side 81 could define the air or gas side within a turbine engine.
  • the lower pressure side 82 could define the bearing or oil side within a turbine engine.
  • outward facing sealing surface 60 along the ceramic runner 52 and annular surface 107 of the carrier 91 are shown approximately radially aligned with the outer diameter 100 of the shaft 57.
  • outward facing sealing surface 60 and annular surface 107 could extend above or be depressed below the outer diameter 100 in other embodiments of the invention.
  • the circumferential seal 46 is illustrated for descriptive purposes along an upper half of an exemplary shaft 57 along a turbine engine rotatable about a centerline 67.
  • a ceramic runner 52 is attached to a carrier 91 to form a cartridge 90.
  • the cartridge 90 facilitates assembly of components comprising the circumferential seal 46 prior to attachment to a shaft 57. This approach simplifies assembly and repair of a turbine engine.
  • the outer diameter 100 of the shaft 57 is shown including a recess 98.
  • the recess 98 could include one or more regions along the shaft 57 each having a diameter smaller than the outer diameter 100.
  • the exemplary shaft 57 has a recess 98 which includes a single section to accommodate a locking ring 75 and a carrier 91 , the latter supporting a ceramic runner 52 and a clamping ring 74.
  • the clamping ring 74 and locking ring 75 are composed of materials suitable for use within a turbine engine. Materials should be wear, failure, and temperature resistant. Exemplary compositions include metals, preferably compositions of steel.
  • the locking ring 75 secures the carrier 91 with the various components described herein to the shaft 57 about the recess 98. It is understood that the recess 98 could include one or more sections as well as other shapes and designs which facilitate attachment of elements required to provide circumferential sealing along a shaft 57.
  • the interface between the outer diameter 100 of the shaft 57 and the outer diameter 62 of the recess 98 defines a first shoulder 55.
  • the recess 98 could include additional shoulders depending on the profile of the recess 98, although such features are optional and design dependent.
  • the recess 98 could include other shoulders each defined by a discontinuity where two outer diameters differ.
  • the carrier 91 is a ring-shaped element with a flange 104 which extends perpendicular from one end an annular ring 105.
  • a clearance fit is provided for assembly purposes between the outer diameter 62 of the shaft 57 and inner diameter 85 of the carrier 91 so that the carrier 91 is slidable with respect to the shaft 57.
  • an interference fit is provided between the outer diameter 62 and the inner diameter 85 and the carrier 91 is heated to open the inner diameter 85 prior to sliding the carrier 91 onto the shaft 57.
  • the carrier 91 is then cooled to fix the carrier 91 to the shaft 57.
  • the flange 104 should contact the shoulder 55 in addition to the annular ring 105 contacting the surface of the shaft 57.
  • the carrier 91 is composed of materials suitable for use within a turbine engine. Materials should be wear, failure, and temperature resistant. Exemplary compositions include metals, preferably compositions of steel with a coefficient of thermal expansion comparable to that of the shaft 57 so that carrier 91 tracks the expansion and contraction of the shaft 57.
  • the carrier 91 could likewise include one or more shoulders along the annular ring 105.
  • the interface between the annular surface 107 along the carrier 91 and the outer diameter 106 of the carrier 91 defines a first shoulder 92.
  • the carrier 91 could also include a first segment with an outer diameter 106 and a second segment with an outer diameter 86.
  • the outer diameter 106 could be larger than the other outer diameter 86 so that a second shoulder 103 is provided at the discontinuity between the two outer surfaces.
  • a clearance fit could be provided between the outer diameter 86 of the carrier 91 and inner diameter 83 along the clamping ring 74 so that the clamping ring 74 is slidable with respect to the carrier 91.
  • the carrier 91 and clamping ring 74 are secured to the shaft 57 via the locking ring 75.
  • the locking ring 75 contacts both the clamping ring 74 and the end 93 of the carrier 91 as illustrate in FIG. 9a.
  • the locking ring 75 includes threads along its inner diameter 84 which engage a complementary thread arrangement along the outer diameter 80 of the shaft 57. The force applied by the locking ring 75 onto the carrier 91 and clamping ring 74 should be sufficient to prevent relative motion with respect to the shaft 57.
  • the ceramic runner 52 is a cylindrically-shaped or sleeve-shaped element which is slid onto the shaft 57 during assembly so as to circumscribe the carrier 91.
  • the ceramic runner 52 is composed of a ceramic composition suitable for use within a turbine engine. In preferred embodiments, the ceramic composition should be wear, failure, and temperature resistant. Exemplary, non-limiting compositions include silicon nitride and silicon carbide.
  • the ceramic runner 52 has an inner diameter 61 which is larger than the outer diameter 106 of the carrier 91 resulting in a second annular gap 72 which avoids direct contact between the ceramic runner 52 and carrier 91.
  • the distance between a first end 53 and a second end 54 of the ceramic runner 52 is less than the axial distance between the first shoulder 92 and second shoulder 103.
  • the first end 53 is positioned adjacent to the first shoulder 92 so that a first annular gap 73 separates the first end 53 from the first shoulder 92.
  • the axial length of the first annular gap 73 is sized to accommodate a spring mechanism.
  • the spring mechanism provides no sealing functionality. Although spring mechanisms are described herein, it is understood that such mechanisms could include other non-sealing devices which at least resist compression and are resilient.
  • the second end 54 directly contacts the clamping ring 74 so that the second end 54 is generally aligned with the second shoulder 103.
  • the spring mechanism could include a plurality of compression springs 88 as represented in FIG. 9a and generally described in FIGS. 7b and 7c.
  • Each compression spring 88 is axially aligned along the direction of the shaft 57.
  • the compression springs 88 are further separately disposed about the shaft 57 along the flange 104 of the carrier 91, as generally shown in FIG. 8c, so as to communicate a biasing force 99 symmetrically about the ceramic runner 52 in the axial direction.
  • One end of each compression spring 88 could reside within a complementary shaped hole 94 within the flange 104 so that a portion of the compression spring 88 extends into the first annular gap 73 with sufficient length to contact the first end 53 along the ceramic runner 52.
  • the compression spring 88 could be mechanically fixed to the hole 94 via an interference fit or freely movable within the hole 94.
  • the compression springs 88 are preferred to be sufficiently long so that each is partially compressed when assembled between the carrier 91 and ceramic runner 52. Partial compression of the compression spring 88 maintains a biasing force 99 onto the ceramic runner 52 so that the second end 54 of the ceramic runner 52 is biased toward and contacts the clamping ring 74.
  • the biasing force 99 maintains contact between the second end 54 of the ceramic runner 52 and the clamping ring 74 during operation of a turbine engine, thereby avoiding separation thereof because of thermally induced expansion and contraction of ceramic runner 52 and other components within the engine.
  • the biasing force 99 is also resists rotational sliding between the ceramic runner 52 and clamping ring 74 at the second end 54.
  • the compression springs 88 are partially compressed at or below ambient conditions so as to allow for further compression of the compression springs 88 during operation of a turbine engine. This feature allows the compression springs 88 to expand and contract with expansion and contraction of the ceramic runner 52 as the ceramic runner 52 and other components heat and cool.
  • the spring mechanism could be a single annular spring 58, as represented in FIG. 8d.
  • Exemplary annular springs 58 include a wave spring or a compression spring or the like which circumscribe the shaft 57 within the first annular gap 73 between the first end 53 of the ceramic runner 52 and first shoulder 92 along the carrier 91.
  • the length of the annular spring 58 in its uncompressed state requires the annular spring 58 to be partially compressed when assembled between the ceramic runner 52 and carrier 91.
  • the annular spring 58 is compressed by contact with the first shoulder 92 at one side of the annular spring 58 and the first end 53 at another side of the annular spring 58.
  • the annular spring 58 communicates a biasing force 99 axially onto the ceramic runner 52 thereby pressing the ceramic runner 52 onto the clamping ring 74.
  • the biasing force 99 is preferred to maintain contact between the second end 54 of the ceramic runner 52 and the clamping ring 74 during operation of a turbine engine, thereby avoiding separation between the ceramic runner 52 and clamping ring 74 which could occur because of thermally induced expansion and contraction of components within the engine.
  • the biasing force 99 also resists rotational sliding motion between the ceramic runner 52 and the clamping ring 74 at the second end 54.
  • the annular spring 58 is partially compressed at or below ambient conditions so as to allow for further compression of the annular spring 58 during operation of a turbine engine. This feature allows the annular spring 58 to expand and contract with axial expansion and contraction of the ceramic runner 52 as the ceramic runner 52 and other components heat and cool.
  • the first end 53 could directly contact the first shoulder 92 and the spring mechanism, either the annular spring 58 or the compression springs 88, is disposed between the second end 54 and clamping ring 74, as shown in FIG. 9e.
  • the biasing force 99 is directed toward the flange 104.
  • the spring mechanisms could be attached to the clamping ring 74 via in a similar manner as the attachment to the flange 104 as described in FIG. 9a.
  • the first annular gap 73 is now disposed between the clamping ring 74 and second end 54.
  • the second annular gap 72 between the inner diameter 61 of the ceramic runner 52 and outer diameter 106 of the carrier 91 is shown with a tolerance ring 70.
  • a tolerance ring 70 is generally described as a ring-shaped element with corrugations along an inward face or an outward face and with a gap 87, the latter feature represented in FIG. 6c.
  • the tolerance ring 70 provides no sealing
  • the tolerance ring 70 When attached between the inner diameter 61 and outer diameter 106 along the gap 72, the tolerance ring 70 conforms to the bore and is self-retaining thereby resisting rotational slip between the ceramic runner 52 and carrier 91.
  • the tolerance ring 70 could allow for axial slippage so as to avoid stresses within the ceramic runner 52.
  • An exemplary tolerance ring 70 is the BN Series devices sold by USA Tolerance Rings of Pennington, New Jersey (United States).
  • the tolerance ring 70 maintains proper fit between the ceramic runner 52 and carrier 91 by expanding circumferentially to the radial clearance between the inner diameter 61 and outer diameter 106 by closing the gap 87. This functionality avoids radial expansion of the ceramic runner 52, which could damage the runner 52.
  • the tolerance ring 70 resides within an annular groove 63.
  • the annular groove 63 could be disposed along the inner diameter 61 of the ceramic runner 52 in an arrangement similar to that shown in FIG. 6a or along the outer diameter 106 of the carrier 91 as shown in FIG. 9a.
  • the depth of the annular groove 63 should allow assembly of the ceramic runner 52 onto the carrier 91 and proper placement of the tolerance ring 70 along the carrier 91 while ensuring sufficient contact between the tolerance ring 70 and inner and outer diameters 61, 106 for proper function of the tolerance ring 70.
  • the annular groove 63 should be at least as wide as the tolerance ring 70, preferably providing a tolerance fit allowing the tolerance ring 70 to be secured within the annular groove 63.
  • the second annular gap 72 between the inner diameter 61 of the ceramic runner 52 and outer diameter 106 of the carrier 91 is shown with a sealing ring 68.
  • the clamping ring 74 also includes a sealing ring 69 disposed along the vertical surface at the interface with the ceramic runner 52.
  • the seal ring 69 could be disposed within an annular groove 66 between the carrier 91 and the ceramic runner 52 along the second annular gap 72 further between the clamping ring 74 and anti-rotation screw 96, as shown in FIG. 9d.
  • Sealing rings 68, 69 could include devices known within the art, examples including, but not limited to, multi-directional O-rings, unidirectional spring-energized seals, high-temperature metallic seal rings, or other comparable devices sold by the Parker Hannifin Corporation located in North Haven, Connecticut (United States) or other suppliers.
  • Other exemplary seals include those sold under the Trademark
  • the sealing ring 68 When assembled between the inner diameter 61 and outer diameter 106 along the second annular gap 72, the sealing ring 68 conforms to the bore thereby further resisting rotational slip between the ceramic runner 52 and carrier 91.
  • the sealing ring 68 could allow for axial slippage so as to avoid stresses within the ceramic runner 52.
  • the sealing ring 69 conforms to the ring-shaped surfaces to further resist rotational slip when assembled between the clamping ring 74 and the ceramic runner 52.
  • Each sealing ring 68, 69 resides within an annular groove 64, 66, respectively.
  • the annular groove 64 could be disposed along the inner diameter 61 of the ceramic runner 52 in an arrangement similar to that shown in FIG. 6a or along the outer diameter 106 of the carrier 91 as shown in FIG. 9a.
  • the depth of each annular groove 64, 66 should be sufficiently deep so as to allow assembly of the ceramic runner 52 onto the carrier 91 and proper placement of the sealing rings 68, 69 along the carrier 91 while ensuring sufficient contact between the sealing ring 68 and inner and outer diameters 61, 106, as well as the sealing ring 69 and the ceramic runner 52 and clamping ring 74, for proper function of the sealing rings 68, 69.
  • the grooves 64, 66 should be at least as wide as the sealing rings 68, 69, preferably with a tolerance fit allowing each sealing ring 68, 69 to be secured within the respective annular groove 64, 66.
  • the sealing rings 68, 69 are disposed about the tolerance ring 70, as represented in FIG. 9a.
  • the sealing rings 68, 69 are oriented so that the sealing direction 101 avoids or at least minimizes oil and other contaminants within the higher and/or lower pressure sides 81 , 82 from entering the second annular gap 72 and interacting with the tolerance ring 70. This feature minimizes degradation to the performance of the tolerance rings 70 caused by oil and other contaminants and further minimizes oil coking under the ceramic runner 52.
  • the carrier 91 further includes at least one anti- rotation screw 96.
  • the anti -rotation screw 96 is attached or fixed to a threaded hole 95 along the carrier 91, as represented in FIG. 9b, via techniques understood in the art so that a portion of the anti-rotation screw 96 extends toward the ceramic runner 52.
  • the end of the anti-rotation screw 96 extending from the carrier 91 could reside within a hole or slot 97 along the ceramic runner 52.
  • the hole or slot 97 could extend from the inner diameter 61 of the ceramic runner 52 and partially traverse the thickness of the ceramic runner 52 in the direction of the outward facing sealing surface 60.
  • the hole or slot 97 is dimensioned to avoid contact with the end and side of the anti-rotation screw 96, see FIGS. 9a and 9c, respectively.
  • the anti-rotation screw 96 could contact a side of the hole or slot 97 when the ceramic runner 52 rotates relative to the carrier 91.
  • the degree of rotation before contact between the anti-rotation screw 96 and side of the threaded hole 95 is determined by the clearance therebetween which is design dependent.
  • An annular seal ring 49 is circumferentially disposed about the outward facing sealing surface 60 of the ceramic runner 52.
  • the annular seal ring 49 includes an inward facing sealing surface 59 which interacts with the outward facing sealing surface 60 to form the circumferential sealing of the present invention.
  • the annular seal ring 49 is a ring-shaped element with or without segmentation.
  • the inward facing sealing surface 59 could physically contact the outward facing sealing surface 60 during rotation of the ceramic runner 52 and shaft 57 to provide a contact seal.
  • the inward facing sealing surface 59 and outward facing sealing surface 60 could be separated by a gap to form a non- contact seal.
  • the outward facing sealing surface 60 could include hydrodynamic pockets which form a thin-film between inward and outward facing sealing surfaces 59, 60 during rotation of the ceramic runner 52.
  • the annular seal ring 49 resides within a seal housing 47 and is secured thereto via a support ring 50 and a retaining ring 51 or other like elements via methods and designs known within the art.
  • the annular seal ring 49 is rotationally stationary with respect to the seal housing 47. As such, the annular seal ring 49 does not rotate with respect to the seal housing 47.
  • the annular seal ring 49 could move radially inward and outward to track radial excursions of the ceramic runner 52.
  • the seal housing 47 is secured to a housing 48 comprising a turbine engine. Both seal housing 47 and housing 48 are shown in a generalized form for descriptive purposes only and are not intended to limit the scope of the claimed invention.
  • Arrangement of the annular seal ring 49, seal housing 47, and housing 48 about the ceramic runner 52 and shaft 57 generally defines a higher pressure side 81 and a lower pressure side 82.
  • the higher pressure side 81 could define the air or gas side within a turbine engine.
  • the lower pressure side 82 could define the bearing or oil side within a turbine engine.
  • outward facing sealing surface 60 along the ceramic runner 52 and annular surface 107 of the carrier 91 are shown approximately radially aligned with the outer diameter 100 of the shaft 57.
  • outward facing sealing surface 60 and annular surface 107 could extend above or be depressed below the outer diameter 100 in other embodiments of the invention.
  • the invention is applicable for use within a variety of applications wherein sealing is required about a rotatable element.
  • a turbine engine including a circumferential seal formed between a stationary annular seal and a rotatable runner.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Materials Engineering (AREA)
  • Mechanical Sealing (AREA)

Abstract

L'invention porte sur un joint circonférentiel (46) applicable aux moteurs à turbine. Le joint circonférentiel (46) comprend un patin en céramique, une bague de joint annulaire (49), au moins une bague de tolérance (70, 71) et une paire de bagues d'étanchéité (68, 69). Le patin (52) entoure un arbre (57) ou d'un élément de support (91) dans un évidement (98) le long de l'arbre (57) et est limité par un épaulement (55 ou 92) et une bague de serrage (74). Au moins un mécanisme à ressort sans fonction d'étanchéité (58 ou 88) est disposé entre l'épaulement (55 ou 92) et la première extrémité (53) du patin (52) et est en contact direct avec ceux-ci. Une seconde extrémité (54) du patin (52) est en contact direct avec la bague de serrage (74). Dans d'autres modes de réalisation, au moins un mécanisme à ressort sans fonction d'étanchéité (58 ou 88) est disposé entre la seconde extrémité (54) et la bague de serrage (74) et est en contact direct avec celles-ci, et la première extrémité (53) est en contact direct avec l'épaulement (55 ou 92). Un élément anti-rotation (76, 89 ou 96) est attaché à la bague de serrage (74), à l'élément de support (91) ou à l'arbre (57) et s'étend dans une fente (78) ou un trou ou une fente (97) le long du patin (52). Le ou les ressorts (58 ou 88) appliquent une force de sollicitation (99) au patin (52) vers la bague de serrage (74) ou l'épaulement (55 ou 92). La bague de joint annulaire (49) est fixe en rotation et entoure le patin (52). La ou les bagues de tolérance (70, 71) sont en contact direct avec le patin (52) et l'arbre (57). Le patin (52) est fixé à l'arbre (57) ou à l'élément de support (91) par l'intermédiaire de la ou des bagues de tolérance (70, 71), de l'élément anti-rotation (76, 89 ou 96) et du ou des ressorts (58 ou 88) de telle sorte que le patin (52) tourne avec l'arbre (57). Les bagues d'étanchéité (68, 69) sont en contact direct avec le patin (52) et l'arbre (57) le long du vide annulaire (72) autour de la ou des bagues de tolérance (70, 71).
PCT/US2013/040812 2013-03-15 2013-05-13 Joint circonférentiel avec patin en céramique WO2014143097A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US14/130,511 US20140265151A1 (en) 2013-03-15 2013-05-13 Circumferential Seal with Ceramic Runner

Applications Claiming Priority (2)

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US201361789419P 2013-03-15 2013-03-15
US61/789,419 2013-03-15

Publications (1)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10927960B2 (en) 2019-02-01 2021-02-23 Rolls-Royce Corporation Mounting assembly for a ceramic seal runner
US10935142B2 (en) 2019-02-01 2021-03-02 Rolls-Royce Corporation Mounting assembly for a ceramic seal runner
US11193590B2 (en) 2019-01-14 2021-12-07 Rolls-Royce Corporation Seal assembly with buffered lip seal
US11415225B2 (en) 2019-05-22 2022-08-16 Rolls-Royce Corporation Seal assembly with deflecting runner mount assembly
EP4063616A1 (fr) * 2021-03-23 2022-09-28 Pratt & Whitney Canada Corp. Ensemble rotor amorti
US11466584B1 (en) 2021-07-29 2022-10-11 Rolls-Royce Corporation Ceramic runner seal assembly with compliant holder

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5301957A (en) * 1992-04-27 1994-04-12 General Electric Company Expanding circumferential seal with upper-cooled runner
US5593165A (en) * 1994-09-20 1997-01-14 Allison Engine Company, Inc. Circumferential flow channel for carbon seal runner cooling
US5813830A (en) * 1996-02-09 1998-09-29 Allison Engine Company, Inc. Carbon seal contaminant barrier system
US6145840A (en) * 1995-06-02 2000-11-14 Stein Seal Company Radial flow seals for rotating shafts which deliberately induce turbulent flow along the seal gap
US20090142180A1 (en) * 2007-11-29 2009-06-04 John Munson Circumferential sealing arrangement

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5301957A (en) * 1992-04-27 1994-04-12 General Electric Company Expanding circumferential seal with upper-cooled runner
US5593165A (en) * 1994-09-20 1997-01-14 Allison Engine Company, Inc. Circumferential flow channel for carbon seal runner cooling
US6145840A (en) * 1995-06-02 2000-11-14 Stein Seal Company Radial flow seals for rotating shafts which deliberately induce turbulent flow along the seal gap
US5813830A (en) * 1996-02-09 1998-09-29 Allison Engine Company, Inc. Carbon seal contaminant barrier system
US20090142180A1 (en) * 2007-11-29 2009-06-04 John Munson Circumferential sealing arrangement

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11193590B2 (en) 2019-01-14 2021-12-07 Rolls-Royce Corporation Seal assembly with buffered lip seal
US10927960B2 (en) 2019-02-01 2021-02-23 Rolls-Royce Corporation Mounting assembly for a ceramic seal runner
US10935142B2 (en) 2019-02-01 2021-03-02 Rolls-Royce Corporation Mounting assembly for a ceramic seal runner
US11415225B2 (en) 2019-05-22 2022-08-16 Rolls-Royce Corporation Seal assembly with deflecting runner mount assembly
EP4063616A1 (fr) * 2021-03-23 2022-09-28 Pratt & Whitney Canada Corp. Ensemble rotor amorti
US11466584B1 (en) 2021-07-29 2022-10-11 Rolls-Royce Corporation Ceramic runner seal assembly with compliant holder

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