Adaptive blade tip seal assembly

Abstract

A high-efficiency compressor section (10) for a gas turbine engine is disclosed. The compressor section includes a vane carrier (12) adapted to hold ring segment assemblies (16) that provide optimized blade tip gaps (28,29) during a variety of operating conditions. The ring segment assemblies include backing elements (30) and tip-facing, elements (32) urged into a preferred orientation by biasing elements (40) that maintain contact along engagement surfaces (44,46). The backing and tip-facing, elements have thermal properties sufficiently different to allow relative growth and geometric properties strategically selected to strategically form an interface gap therebetween (42) resulting in blade tip gaps that are dynamically adjusted operation.

Claims

1. A gas turbine engine having a compressor section optimized to provide enhanced efficiency during several operating conditions, said compressor section comprising: a vane carrier; a ring segment assembly disposed within said vane carrier, said ring segment assembly characterized by a radially-outward backing element, a radially-inward tip-facing element, and at last one biasing element adapted and arranged to dynamically position said tip-facing element with respect to said backing element, said ring segment assembly being characterized by an arcuate ring segment angle; wherein said backing element is characterized by a first coefficient of thermal expansion and said tip-facing element is characterized by a second coefficient of thermal expansion, said first coefficient of thermal expansion being higher than said second coefficient of thermal expansion; wherein said backing element includes a first mating surface characterized by an interface angle and said tip-facing element includes a second mating surface, said mating surfaces adapted and arranged to provide positive engagement; wherein said backing element and said tip-facing element cooperate with said at least one biasing element to urge said tip-facing element and said backing element into said positive engagement; wherein said at least one biasing element and said interface angle are selected to provide a biasing force sufficient to overcome a friction force generated along the first and second mating surfaces; whereby said tip-facing element and said backing element are alternately in contact along an interface disposed therebetween during a first operating condition and spaced apart along an interface gap disposed therebetween during a second operating condition, and whereby said at least one biasing element maintains contact between said first and second mating surfaces during both operating conditions.

2. The gas turbine engine of claim 1, wherein said backing element is made from high alpha stainless steel.

3. The gas turbine engine of claim 2, wherein said tip-facing element is made from low alpha stainless steel.

4. The gas turbine engine of claim 1, wherein said second operating condition is steady state operation characterized by temperatures sufficient to form said interface gap.

5. The gas turbine engine of claim 1, wherein said coefficient of friction is 0.73 or higher.

6. The gas turbine engine of claim 1, wherein the difference between said interface angle and said ring segment angle* is about 35 degrees or less.

Description

BRIEF DESCRIPTION OF THE DRAWING

(1) FIG. 1 is a side elevation of a gas turbine engine compressor section employing the ring segment assembly of the present invention;

(2) FIG. 2 is a side sectional view of a blade tip, ring segment assembly, and blade tip gap of the present invention during an initial, cold build condition;

(3) FIG. 3 is a side sectional view of a blade tip, ring segment assembly, and blade tip gap of the present invention during a steady-state operating mode;

(4) FIG. 4 is a close-up view of the ring segment assembly of the present invention, taken along cutting line IV-IV;

(5) FIG. 5 is schematic diagram showing force resolution within the ring segment assembly of the present invention;

(6) FIG. 6 is a table showing a relationship among allowable angles and coefficients of friction within the ring segment assembly of the present invention;

(7) FIG. 7 is a side sectional view of a blade tip, ring segment assembly, and blade tip gap of the present invention during an initial, cold build condition, taken along cutting line VII-VII;

(8) FIG. 8 is an alternate side sectional view of a blade tip, ring segment assembly, and blade tip gap of FIG. 7, shown in a steady-state operating mode;

(9) FIG. 9 is a close-up view of the ring segment assembly of the present invention, taken along cutting line IX-IX;

(10) FIG. 10 is schematic diagram showing force resolution within the ring segment assembly of the present invention; and

(11) FIG. 11 is a table showing a relationship among allowable angles and coefficients of friction within the ring segment assembly of the present invention.

DETAILED DESCRIPTION OF THE INVENTION

(12) Reference is now made in general to the Figures, and to FIG. 1, in particular, wherein the compressor section 10 of the present invention is shown. The compressor section 10 includes several stages of fixed vanes 18 and rotating blades 20the vanes 18 are fixed within vane mounting slots 22 in vane carriers 12, and blades 20 are fixed within a longitudinally-aligned rotor 24 that spins about a central axis during operation. In a longitudinal, flow wise direction, the vane carriers 12 typically span several stages. As shown in FIG. 4, each is vane carrier has generally arcuate cross section when cut in a plane perpendicular to the center axis of the compressor rotor 24, and several are distributed circumferentially around the rotor 24 to form a bounded flow path 25 for compressed air to follow during operation. Although only one blade 20 and vane 18 is shown per stage, each stage will contain multiple blades and vanes distributed circumferentially within the bounded flow path 25.

(13) Ring segment assemblies 16 are also mounted within the vane carriers 12. As shown more fully in FIGS. 2 and 3, the ring segment assemblies 16 are multi-layered and include a radially-outward backing element or plate 30 and a radially-inward tip-facing element 32 positioned proximate the tips 26 of the rotating blades 20 during operation. An optional abradable coating layer 34 may be positioned radially inward of the tip-facing element 32 to accommodate occasional blade tip contact. With continued reference to FIGS. 2 and 3, the radial space between the ring segment assemblies 16 and blade tips 26 defines a performance-impacting blade tip gap 28. As will be described more fully below, optimizing the size of these blade tip gaps 28 during the several engine operation modes improves engine overall efficiency and is an object of this invention.

(14) In FIG. 2, a blade tip 26 is shown proximate a ring segment assembly 16 in a steady-state operating condition. In this condition, compressor components are generally considered to be thermally saturated, with the compressor components having reached an optimized level of thermally-driven component growth. In this steady state condition, a desired tip gap 28 exists between the ring segment assembly 16 and the various blade tips 26 of the blades 20 mounted on the circumferentially spinning rotor 24.

(15) In FIG. 3, the blade tip 26 is shown proximate a ring segment assembly 16 in a hot restart operating condition. In this condition, compressor components are no longer considered to be thermally saturated: due to variations in thermal growth tendencies, some components (like the ring segment assemblies 16) will have partially cooled and shrunk radially inward, while other components (like the rotating blades 20), will likely not have cooled. In this condition, a hot restart blade tip gap 29 exists, but it is typically larger than the steady-state blade tip gap 28.

(16) In one embodiment of this invention, the backing element 30 and tip-facing element 32 are adapted and arranged to passively optimize the tip gaps 28, 29 present during steady-state (shown in FIG. 5) and hot restart conditions (shown in FIG. 6). In a preferred embodiment, the backing element 30 is more thermally reactive than the tip-facing element 32. In one arrangement, the backing element is made from a high alpha material (such as 304 stainless steel or thermal equivalent), while the tip-facing element is made from a low alpha material (such as 410 stainless steel or thermal equivalent). Additionally, with collective reference to FIGS. 4, 5, and 6, each backing element 30 and tip-facing element 32 respectively include positioning notches 44, 46 that, together with biasing elements 40, urge the backing and tip-facing elements into a tip-gap optimizing arrangement during the various operating conditions, as described more fully below.

(17) During operation, the backing element 30 adopts several orientations due to differing thermal loads. For example the backing element shifts from a circumferentially-expanded and radially-compact orientation in the steady state condition shown in FIG. 5, to a circumferentially compact and radially expanded orientation in the hot restart condition shown in FIG. 6.

(18) During steady state operating conditions, the backing elements 30 and tip-facing element 32 are spaced apart by an interface gap 42, and the associated positioning notches 44,46 cooperate with the biasing elements 40 shown in FIG. 2 to urge the backing elements and tip-facing element into positive engagement. This positive engagement creates and maintains a desired steady-state tip gap 28 that is large enough to avoid component damaging contact while small enough to provide efficient compressed airflow.

(19) During hot restart conditions, the backing elements 30 and tip-facing element 32 are spaced apart by an interface 43, and the associated positioning notches 44,46 cooperatively urge the backing elements and tip-facing element into positive engagement. This positive engagement creates and maintains a desired hot restart tip gap 29 that is large enough to avoid component damaging contact while small enough to provide efficient compressed air flow.

(20) With reference to FIG. 7, a blade tip 26, ring segment assembly 16, and blade tip gap 29 of the present invention will be described in a initial, cold build condition. The abradable coating layer 34 is safely spaced away from the blade tips 26, but the tip gap is 29 it too large for efficient operation.

(21) Now with reference to FIG. 8, a blade tip 26, ring segment assembly 16, and blade tip gap 28 of the present invention will be described during steady-state operating condition. The abradable coating layer 34 is safely spaced away from the blade tips 26, but thermal growth of the backing element 30 has caused the backing element positioning notch 44 to shift circumferentially away from tip-facing element positioning notch 46, thereby allowing the biasing element 40 to force the tip-facing element 32 away from the 30, creating an interface gap 42 and reducing the blade tip gap by an amount substantially equal to the radial height of interface gap 42.

(22) Operation of this invention benefits from properly matching aspects of the backing element notch 44 and tip-facing notch 46. This concept will be described in more detail here, with additional reference to FIGS. 9, 10, and 11. In particular, is important that angles and be selected as compatible pairs, as follows: to avoid thermal lockup between the interface positioning notches 44,46, the following equations must be satisfied. The normal components from spring load Ps equals that of thermal contact load P, then N=Ps*cos ()=P*sin (). Then the shear component of P must be greater than the shear component of Ps plus the friction component, N, or P*cos ()Ps*sin ()+*Ps*cos (). Solving for , the friction coefficient is c tan()tan(), where is the wedge angle, and is of the ring segment angle (the ring segment angle is the arcuate distance in degrees between ring segment ends 48, 50 shown in FIG. 4). For a 45 degree ring segment and 45 degree wedge angle, the allowable friction coefficient, , must be less than c tan(22.5)tan(22.5)=2. For a 60 degree ring segment and 50 degree wedge angle, the friction coefficient, , must be less than c tan(20)tan(20)=2.38. As of the components chosen decreases, likelihood of notch lockup increases, as the urging capacity of the biasing elements is no longer sufficient to overcome the friction between the backing element positioning notch 44 and the tip-facing element positioning notch 46, at which point the design would not function reliably. A value () of 35 degrees or lower is preferred and corresponds to a coefficient of friction of 0.73, although other values may be selected, if chosen to match the biasing characteristics of the biasing elements 40.

(23) It is to be understood that while certain forms of the invention have been illustrated and described, it is not to be limited to the specific forms or arrangement of parts herein described and shown. It will be apparent to those skilled in the art that various, including modifications, rearrangements and substitutions, may be made without departing from the scope of this invention and the invention is not to be considered limited to what is shown in the drawings and described in the specification. The scope if the invention is defined by the claims appended hereto.