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    • 专利摘要:
    A variable orifice assembly (20) for a compressor (12) is described having a plurality of variable pitch vanes (22). The Verstellleitapparatanordnung (20) has a synchronizing ring (26) and a plurality of fastening bolts (58) which are secured to the synchronizing ring (26). The Verstellleitapparatanordnung (20) also has a plurality of lever arms (24), wherein each lever arm (24) has a first end (66) and a second end (68). The first end (66) of each lever arm (24) is attached to one of the variable pitch vanes (22). In addition, a plurality of pivotal fasteners (60) are configured to connect the second end (68) of each lever arm (24) with a respective mounting bolt (58) to define a rotational movement interface therebetween. For this purpose, each of the fastening bolts (58) is rigidly fastened to a component of the rotary fastening devices (60).
    公开号:CH703871B1
    申请号:CH01568/11
    申请日:2011-09-21
    公开日:2016-04-15
    发明作者:Mcfarland Jarrett Harry Jr；Velampati Jayakrishna；John Lammas Andrew
    申请人:Gen Electric；
    IPC主号:
    专利说明:

    Field of the invention
    The present subject matter relates generally to gas turbines, and more particularly to a variable orifice assembly for a compressor having a plurality of blades.
    Background of the invention
    Gas turbines usually have a compressor, a plurality of combustion chambers and a turbine section. The compressor puts air under pressure. The pressurized air discharged from the compressor flows into the combustion chambers. Air is mixed with the fuel and burned. Hot combustion gases flow from each combustion chamber through a transition piece to the turbine section of the gas turbine to drive the turbine and generate power.
    A typical compressor for a gas turbine may be configured as an axial multi-stage compressor and may include both rotating and stationary components. A shaft drives a main rotor drum or wheel that has multiple ring rotors. Rotor stages of the compressor rotate between a similar number of stationary stator stages, each rotor stage having a plurality of rotor blades secured to the rotor wheel. Each stator stage has a plurality of secured on an outer casing of the compressor Verstellleitschaufeln. During operation, the airflow passes through the compressor stages and is progressively compressed, with each successive downstream stage increasing the pressure until the air is discharged from the compressor discharge at a maximum pressure.
    To improve the performance of a compressor, one or more of the stator stages may include variable pitch vanes adapted to be rotated about their longitudinal or radial axes. Such variable displacement vanes generally allow for an increase in compressor efficiency and operability by controlling the amount of air flowing into and through the compressor by altering the angle at which the variable direction vanes are oriented toward the airflow. The rotation of the variable capacity vanes is generally accomplished by attaching a lever arm to each variable speed vane and connecting each lever to a synchronizing ring disposed substantially concentrically with respect to the compressor housing. The synchronizing ring is in turn connected to an actuator which is adapted to rotate the ring about the main axis of the compressor. As the synchronizing ring is rotated by the actuator, the lever arms are pivoted accordingly, causing each adjusting vane to rotate about its radial or longitudinal axis.
    A conventional synchronizer ring and the lever arm components are generally configured so that the lever arms at the rotational movement interface between such components have a sliding engagement with the synchronizer ring. In particular, the lever arm is normally adapted to slide radially and / or circumferentially at the rotational movement interface between the lever arm and the synchronizing ring when the ring is twisted. This sliding engagement generally creates excessive wear on the components of the structure disposed on this sliding interface. In addition, the sliding engagement, which is often used in conventional components, provides inadequate support for the synchronizer ring. In particular, the lever arms which are arranged on the upper side of the synchronizing ring, due to the relative displacement between the lever arms and the synchronizing ring during rotation of the ring no portion of the ring weight. Accordingly, the lever arms arranged around the lower portion of the synchronizing ring must support the full weight of the ring. Such inadequate support can lead to further wear of the components located at the attachment interfaces between the lever arms and the synchronizer ring. Further, inadequate support can also result in excessive wear on the friction blocks disposed about the compressor housing because the friction blocks must be used to support a portion of the ring weight.
    Accordingly, the object underlying the present invention is to provide a Verstellleitapparatanordnung that provides increased support for the synchronizer and also reduces wear. This object is solved by the subject matter of the independent patent claims. Advantageous developments of the present invention are the subject of the dependent claims.
    Brief description of the invention
    Aspects and advantages of the invention will be set forth in part in the description which follows.
    The present invention relates to a Verstellleitapparatanordnung for a compressor having a plurality of blades. The Verstellleitapparatanordnung has a synchronizing ring and a plurality of secured to the synchronizing ring fastening bolts. The Verstellleitapparatanordnung further comprises a plurality of lever arms, wherein each lever arm has a first end and a second end. The first end of each lever arm is attached to one of the blades. In addition, a plurality of pivotal fasteners are configured to connect the second end of each lever arm to one of the mounting bolts to define a rotational motion interface therebetween. Further, each of the mounting bolts is rigidly secured to a component of each one of the pivotal mounting means such that substantially no radial and circumferentially-oriented sliding movement occurs between the synchronizer ring and the lever arms during rotation of the synchronizer ring.
    According to an advantageous embodiment of the present invention, the Verstellleitapparatanordnung a plurality of bearings which form the rotary fastening means and which have an inner component and an outer component which is adapted to rotate with respect to the inner component. The outer component of each bearing is connected to the second end of one of the lever arms. Further, each of the mounting bolts is rigidly secured to the inner component of one of the bearings so that there is no substantial relative movement between the synchronizer ring and the inner components during rotation of the synchronizer ring.
    The present invention also relates to a compressor of a gas turbine. The compressor has a housing and a plurality of at least partially disposed within the housing Verstellleitschaufeln. Each of the plurality of variable direction vanes has a shaft segment extending through the housing. The compressor further comprises a Verstellleitapparatanordnung. The Verstellleitapparatanordnung has a synchronizing ring and a plurality of secured to the synchronizing ring fastening bolts. The Verstellleitapparatanordnung also has a plurality of lever arms, wherein each lever arm has a first end and a second end. The first end of each lever arm is attached to one of the blades. In addition, a plurality of pivotal attachment means is configured to rotatably connect the second end of each lever arm to one of the attachment bolts to define a rotational movement interface therebetween. Further, each of the mounting bolts on the rotary motion interface thus formed is rigidly connected to a component of each of the rotary fasteners so that there is no substantial radial and circumferentially directed sliding relative movement between the synchronizer ring and the lever arms during rotation of the synchronizer ring.
    These and other features and advantages of the present invention will be better understood from the following description and claims. The accompanying drawings, which are incorporated in and constitute a part of the specification, illustrate embodiments of the invention and, together with the description, serve to explain the principles of the invention.
    Brief description of the drawings
    A full, corrective, self-explanatory description of the present invention, including the best mode thereof, is set forth in the description which refers to the accompanying drawings, in which:<Tb> FIG. 1 <SEP> provides a schematic picture of a gas turbine;<Tb> FIG. Figure 2 illustrates a cross-sectional view of one embodiment of a variable orifice assembly in accordance with aspects of the present invention, particularly illustrating the vane recliner assembly connected to one of a plurality of variable orifices of a compressor;<Tb> FIG. Figure 3 shows an enlarged view of part of the embodiment of the vane adjustment assembly illustrated in Figure 2, particularly illustrating the attachment of the lever arm to the synchronizer ring; and<Tb> FIG. Fig. 4 shows a partial perspective view of one embodiment of an adjustable nozzle assembly, particularly illustrating the synchronizer ring and an actuator connected to the synchronizer ring.
    Detailed description of the invention
    [0013] Reference will now be made in detail to embodiments of the invention, one or more examples of which are illustrated in the drawings. Each example is given for explanation of the invention, but not for the purpose of limiting the invention.
    The present invention relates to a Verstellleitapparatanordnung for a turbine compressor. The Verstellleitapparatanordnung has a plurality of lever arms, which are rotatably connected to a synchronizing ring by a plurality of fastening bolts and rotary fastening means. As such, each lever arm is pivotable and / or rotatable with respect to the synchronizer ring via a rotary motion interface defined by one of the pivotal fasteners. In addition, each mounting stud of the variator assembly is rigidly secured to the rotary motion interface on a component of one of the pivotal fasteners such that there is no relative motion or relative relative movement between the synchronizer ring and the rotary motion interface during rotation of the ring. The lever arms are prevented or substantially prevented from sliding radially, circumferentially or in any other direction than the direction of rotation about the fastening bolt with respect to the synchronizing ring. As will be described below, this rigid connection can reduce and / or prevent wear occurring along the locations where the lever arms are connected to the synchronizer ring, and also increase the amount of support provided to the synchronizer ring.
    With reference to the drawings, FIG. 1 illustrates a schematic of a gas turbine 10. The gas turbine 10 generally includes a compressor 12, a plurality of combustors 14, and a turbine section 16. The compressor 12 and the turbine section 16 may be generally connected by a shaft 18. The shaft 18 may be a one-piece shaft or a multi-segmented shaft to form the shaft 18. In one embodiment, the compressor 12 may include an axial multi-stage compressor having a plurality of corresponding rotor and stator stages. In such an embodiment, one or more of the stator stages may include a plurality of variable vanes. For example, the compressor 12 may include a plurality of fixed variable vanes in its downstream stages and variable vanes disposed in upstream stages thereof. Alternatively, all the stator stages of a compressor 12 may comprise variable guide vanes.
    During operation of the gas turbine 10, the compressor 12 supplies compressed air to the combustors 14. In each combustor 14, air and fuel are mixed and hot combustion gas flows in a hot gas path from the combustors 14 to the turbine section 16, where the combustion gases receive energy is withdrawn to produce work.
    Reference is made to FIGS. 2-4; There are illustrated various views of embodiments of a variable orifice assembly 20 which serves to drive multiple variable orifices 22 in accordance with aspects of the present invention. In particular, FIG. 2 illustrates a cross-sectional view of one embodiment of the variable headset assembly 20 described associated with one of the variable pitch vanes 22. FIG. 3 illustrates an enlarged view of a portion of the variable headset assembly 20 illustrated in FIG. 2, particularly the connection of the lever arm 24 to the synchronizer ring 26. In addition, FIG. 4 illustrates a partial perspective view of one embodiment of the variable orifice assembly 20 described, with particular reference to the synchronizer ring 26 and an actuator 28 connected to the synchronizer ring 26.
    As particularly shown in FIG. 2, the compressor 12 of a gas turbine engine 10 includes one or more stator stages having a plurality of variable displacement vanes 22 (one of which is shown) rotatably mounted in an outer compressor housing 30. Each variable vane 22 generally includes a vane portion having a first or pressure side 34 and a circumferentially opposed or second suction side 32 (not shown) which form the aerodynamic surface of the variable speed vane 22 through which air 36 flows during operation of the compressor 12. The pressure side and the suction side generally extend axially along a chord between a leading edge 40 and an opposite trailing edge 42, and extend radially from a radially inner point 44 to a radially outer foot 46. Each variable speed vane 22 also includes a one - piece shank portion 48 extending coaxially and radially away from the blade portion 32 through a complementary cylindrical opening 50 formed in the housing. The shaft segment 48 is rotatably mounted in the opening 50. For example, at the interface between the housing 30 and the stem segment 48, a bushing 52 is disposed to allow the adjustment vane 22 to pivot relative to the housing 30.
    Each variable displacement vane 22 of the compressor 12 is configured to direct the air 36 flowing through the compressor 12 to a corresponding row or stage of rotor blades 54 extending radially outwardly from a rotor disk or wheel 56 carrying them , Specifically, the air 36 passed through each stage of the variable speed vanes 22 and rotor blades 54 is gradually compressed in the compressor 12 and then discharged into the combustion chambers 14 of the gas turbine 10. By varying or rotating the angle at which the variable speed vanes 22 are oriented toward the airflow 36, compressor efficiency and operability are increased by adjusting the amount of air 36 flowing into and through the compressor 12. In order to facilitate such rotation of the adjusting vanes 22, a Verstellleitapparatanordnung 20 can be used, as described in detail below.
    With reference to Figures 2-4, the present variable displacement guide assembly 20 includes a synchronizer ring 26 adapted to drive a plurality of outwardly extending lever arms 24 which mount to each variable stator vane 22 of a compressor 12 of a particular stator stage and are rigidly attached. The synchronizing ring 26 is connected to the lever arms 24 by a plurality of fastening bolts 58 arranged along the circumference of the ring 26. In addition, the Verstellleitapparatanordnung 20 also on a plurality of pivotal mounting means 60 which are arranged between the lever arms 24 and the fastening bolt 58 to define a rotational movement interface 76, via which the lever arms 24 with respect to the fastening bolts 58 and / or the synchronizing ring 26 can be rotated , As more particularly shown in FIG. 4, the synchronizer ring 26 may also be coupled to one or more mating actuators 28 to rotate the synchronizer ring 26 about a major axis 62 of the compressor 12. For example, the synchronizer ring 26 may be connected to the actuator (s) 28 by any suitable means (eg, by a pushrod 64) such that the actuator (s) 28 rotate the synchronizer ring 26 clockwise or counterclockwise about the major axis 62 twist. Because the synchronizer ring 26 is rotated by the actuator (s) 28, the lever arms 24 can correspondingly rotate about the mounting bolts 58. The pivoting lever arms 24, in turn, cause the adjustment vanes 22 to rotate, thereby changing the particular angle at which the variable direction vanes 22 are oriented with respect to the airflow 36 in the compressor 12.
    The synchronizing ring 26 of the Verstellleitapparatanordnung 20 is formed as a circular or ring-like structure, which is arranged radially outwardly and substantially concentric with the compressor housing 30. In various embodiments, the synchronizer ring 26 may be manufactured as a one-piece or multiple-piece construction and may be formed from any suitable material, such as stainless steel or any other material capable of withstanding the forces normally applied to a synchronizer ring. Additionally, the synchronizer ring 26 may generally have any mating cross-section, such as a rectangular, elliptical, or circular cross-sectional shape. As particularly shown in FIGS. 2 and 3, in one embodiment, the synchronizer ring 26 may define a generally "C-shaped" cross-section. As such, the synchronizer ring 26 may be relatively easily formed without compromising the structural integrity of the ring 26.
    Referring more particularly to FIG. 2, each lever arm 24 of the Verstellleitapparatanordnung 20 has a first end 66 which is rigidly secured to the shaft segment 48 of a Verstellleitschaufel 22, and a second end 68 which rotates with the synchronizing ring 26 by a fastening bolt 58 , but relentlessly connected. Generally, the first end 66 of each lever arm 24 may be secured to the variable speed vane 22 by use of any suitable means. For example, in one embodiment, the variable speed vane 22 may include a tread seat 70 (eg, a "D" shaped seat) extending outwardly from the shaft segment 48 along the chord 38 and a threaded shaft 72 extending from the tread seat 70 the tendon 38 extends outwards. The profile seat 70 may be formed so that the lever arm 24 can be mounted self-aligning on top of the Verstellleitschaufel 22. For example, the first end 66 of the lever arm 24 may define a mounting hole (e.g., a D-shaped mounting hole) configured in accordance with the shape of the tread seat 70 to allow the lever arm 24 to be rotationally connected to the adjustable vane 22. The lever arm 24 may then be secured to the variable speed vane 22 by inserting a threaded nut 74, such as a threaded nut. a lock nut or a lock nut, is arranged on the threaded shaft 72.
    It should be apparent to one of ordinary skill in the art that various other configurations may be utilized within the present subject matter to mount and / or rigidly secure the first end 66 of the lever arm 24 to the shank segment 48 of the variable speed vane 22. For example, spline joints, conforming crown molding surfaces, or other mating means may be used to connect or otherwise engage the lever arm 24 with the variable speed vane 22. Similarly, in various embodiments, the lever arm 24 may be secured to the variable speed vane 22 by use of a mounting pin or bolt, weld connection or any other suitable fastening and / or securing means.
    Referring now to Fig. 3; the second end 68 of each lever arm 24 is configured to be rotatably connected to the synchronizer ring 26 by a mounting bolt 58. In particular, between each lever arm 24 and its corresponding mounting bolt 58, a pivotal mounting means 60 is disposed so as to define a rotary motion interface 76 therebetween. Accordingly, the lever arm 24 is allowed to pivot at the interface 76 with respect to the synchronizer ring 26 and / or the mounting bolt 58. Further, each mounting bolt 58 is also configured to be relentlessly attached to a portion of the pivot fastener 60 such that there is no other relative movement (or substantially no other relative movement) between the synchronizer ring 26 and the pivot interface 76 than the rotational movement with which the lever arm 24 rotates about the rotary motion interface 76. As such, the lever arm 24 may be prevented or substantially prevented from sliding during rotation of the ring 26 radially, circumferentially or any other direction relative to the synchronizer ring 26 and / or the mounting bolts 58.
    In one embodiment, to facilitate such pivotal connection and rigid connection of the various constituent elements of the variable displacement guide assembly 20, each attachment bolt 58 may generally include a plurality of segments, such as a lower segment 78, a middle segment 80, an upper segment 82, and a shoulder portion 84. which is arranged between the lower segment 78 and the middle segment 80. As shown in FIG. 3, each of the segments 78, 80, 82, 84 may be generally coaxially aligned along a major axis 86 of the mounting bolt 58. In addition, each of the segments 78, 80, 82, 84 may be substantially cylindrically shaped. However, it should be understood that each segment 78, 80, 82, 84 may generally have any suitable shape that allows the segment 78, 80, 82, 84 to function as described herein. Further, each of the segments 78, 80, 82, 84 may be separated by a groove 88. Such grooves 88 may generally be formed on the mounting bolt 58 to form stretchable regions. In addition, the grooves 88 may serve to enhance the connection of the segments 78, 80, 82, 84 to the various other components of the variable orifice assembly 20. Specifically, the grooves 88 may serve to position or otherwise align the surfaces and / or surfaces of the segments 78, 80, 82, 84 and the other components.
    With continued reference to FIG. 3, the lower segment 78 of the mounting bolt 58 can be generally configured to be secured to a portion of the synchronizer ring 26. For example, in the illustrated embodiment, the lower segment 78 may be secured to a lower extension 90 of the common "C-shaped" synchronizer ring 26 such that the attachment bolt 58 extends substantially radially outwardly therefrom. It should be appreciated that the lower segment 78 may be secured to the synchronizer ring 26 at any other suitable position. For example, lower segment 78 may be secured to an upper extension 92 of synchronizer ring 26 such that mounting stud 58 extends radially outwardly or radially inwardly. Further, in embodiments in which the synchronizer ring 26 does not have a generally "egg-shaped" cross-section, the lower segment 78 can be secured to any mating part of the synchronizer ring 26 that allows the disclosed variable orifice assembly 20 to function as described herein.
    In addition, it should be appreciated that the lower segment 78 of the mounting bolt 58 can generally be secured to the synchronizer ring 26 using any suitable method of connection known in the art. For example, as shown in FIG. 3, the lower segment 78 may be threaded so that it can be secured within a corresponding threaded bore 94 defined in the synchronizer ring 26. In another embodiment, the lower segment 78 may be configured to be press fit, or may be adhesively secured within a corresponding hole (not illustrated) in the synchronizer ring 26.
    Furthermore, with reference to FIG. 3, the middle segment 80 of each fastening bolt 58 can generally serve as a rotary joint between the lever arm 24 and the synchronizer ring 26. As such, the center segment 80 may be configured to receive any suitable pivot fastener 60 known in the art to articulate the lever arm 24 to the synchronizer ring 26 via the mounting stud 58. For example, in the illustrated embodiment, the pivot fastener 60 includes a bearing 61 that is mounted on or otherwise disposed about the middle segment 80 to define a rotational interface 76 between the lever arm 24 and the mounting stud 58. In that regard, it should be appreciated that the center segment 80 may generally have a shape and configuration suitable for receiving the bearing 61. For example, in one embodiment, the center segment 80 may define a smooth cylindrical or seating surface so that the bearing 61 may be mounted thereon. In addition, the middle segment 80 may be sized to achieve a controlled tight fit between the bearing 61 and the mounting bolt 58. For example, the clearance present between the bearing 61 and the middle segment 80 may be less than about 1 millimeter (mm) in diameter, alternatively less than about 0.5 mm in diameter clearance or less than a diameter clearance of about 0.1 mm. In a particular embodiment of the present subject matter, the clearance may range from about 0.01 mm diameter clearance to about 0.07 mm, such as e.g. from about 0.03 mm diameter clearance to about 0.05 mm diameter clearance, as well as all other subranges in between. However, it should be understood that in alternative embodiments, the existing clearance may be greater than a 1mm diameter clearance.
    In general, any suitable bearing known in the art can be used to provide a hinge connection between the lever arm 24 and the mounting bolt 58. As shown in FIG. 3, in one embodiment, the bearing 61 may include a spherical bearing having an inner ball 96 mounted on the middle segment 80 of the mounting bolt 58 and an outer race bore 98 secured within a corresponding hole 100. which is defined at the second end 68 of the lever arm 24. The outer ring bore 98 may generally have an inner concave spherical surface corresponding to the spherical convex outer surface of the inner ball 96 to allow the outer ring bore 98 to rotate in one or more orthogonal directions with respect to the inner ball 96. Thus, when the synchronizer ring 26 is rotated by the actuator 28, each lever arm 24 can rotate and / or pivot about the rotary motion interface 76 defined between the inner ball 96 and outer race bore 98 of the bearing 61.
    It should be apparent to those skilled in the art that within the scope of the present invention various other suitable pivotal fasteners 60 can be utilized to rotatably connect the lever arms 24 to the synchronizer ring 26 about the mounting bolts 58, thus providing a rotary motion interface 76 over which the lever arms 24 with respect to the ring 26 and / or the fastening bolts 58 can rotate. For example, in alternative embodiments, the rotary fastener 60 may include part of a mating hinge such as a ball / socket joint, ellipsoid joint, hinge joint, or the like, mated to the shape formed on the mounting bolt 58 or otherwise specified. Alternatively, the mounting bolt 58 itself may serve as part of the pivotal attachment means 60 of the variable displacement apparatus assembly 20. For example, the lever arm 24 or a component mounted to the lever arm 24 may be configured to pivot directly about the mounting bolt 58 (e.g., about the center segment 80) such that the outer surface of the mounting bolt 58 itself defines the rotary motion interface 76.
    With continued reference to FIG. 3 as above, the second end 68 of the lever arm 24 may also be configured to be so rigidly connected to the synchronizer ring 26 via the mounting bolt 58 that there is no other relative movement or substantial other Relative movement between the synchronizer ring 26 and the rotary motion interface 76 is, as the rotational movement, with which the lever arm 24 pivots. Thus, the upper segment 82 of the mounting bolt 58 may be adapted to receive a fastener 102 configured to allow the pivot fastener 60 to be rigidly secured to the mounting stud 58. For example, as shown in FIG. 3, the inner ball 96 of the bearing 61, which defines the rotational motion interface 76 between the lever arms 24 and the mounting bolts 58, may be rigidly connected to the mounting bolt 58 such that the inner ball 96 rotates upon rotation of the ball Rings 26 does not slide or otherwise moves with respect to the synchronizing ring 26. Specifically, the upper segment 82 of the mounting bolt 58 may be threaded to allow a threaded fastener 102 (e.g., a locknut or locknut) to be secured securely over the inner ball 96 of the bearing 61. In addition, as shown, the shoulder portion 84 of the mounting bolt 58 may extend substantially outwardly from the main axis 86 of the mounting bolt 58 than the middle segment 80, such that the inner ball 96 may be positioned or otherwise positioned against a radially outer surface 104 of the shoulder portion 84 , Insofar as the fastener 102 is secured over the bearing 61, the inner ball 96 may be clamped, pressed, or otherwise rigidly secured between the fastener 102 and the outer surface 104 of the shoulder portion 84 to prevent any relative movement between the synchronizer ring 26 and the rotary motion interface 76. pivots about the lever arm 24. Further, it should be appreciated that the grooves 88 defined in the fastening bolt 58 may be configured to assist in the rigid connection of the inner ball 96 to the fastening bolt 58. For example, the groove 88 may be defined between the shoulder portion 84 and the middle segment 80 to allow the inner ball 96 to be aligned with the outer surface 104 of the shoulder portion 84. Similarly, the groove 88 may be defined defined between the upper segment 82 and the middle segment 80 to allow the threads of the upper segment 82 to be hidden or otherwise disposed entirely within the fastener 102.
    It should also be appreciated that, in alternative embodiments, various other fasteners 102, such as fastener pins, latches, or any other suitable interlocking mechanisms, may be used to rigidly secure the inner ball 96 of the spherical bearing 61 to the mounting stud 58 , Also, other suitable securing / attachment techniques, such as welding, bonding, and the like, may be used to rigidly secure the inner ball 96 to the mounting bolt 58. For example, in one particular embodiment of the present subject matter, a portion of the mounting bolt 58 (e.g., mid-segment 80) may be configured so that the inner ball 96 is press-fit on the mounting bolt 58 to provide a rigid connection therebetween. Additionally, it should be understood that in embodiments where the pivotal connection between the mounting bolt 58 and the lever arms 24 is provided by means other than a bearing 61, similar fasteners 102 and / or securing means may be used to control the relative movement between the synchronizer ring 26 and to prevent the rotary motion interface 76 from rotating about each of the lever arms.
    By the inventive coupling of the synchronizing ring 26 to the lever arms 24 via the respective fastening bolts 58 numerous advantages of Verstellleitapparatanordnung 20 described can be obtained. For example, due to the rigid connection to a portion of the pivot fastener 60, circumferential and radial sliding motions that may otherwise occur between the lever arms 24 and the synchronizer ring 26 may be prevented or at least reduced. In that regard, any wear that occurs on the mounting bolt 58, the bearing 61, the lever arms 24 and / or the synchronizing ring 26 can be significantly reduced and / or prevented. In addition, the inventive coupling of each lever arm 24 to the synchronizing ring 26 ensures that all lever arms 24 carry the weight of the synchronizing ring 26 at its entire circumference. Accordingly, the concentricity or roundness of the synchronizer ring 26 can be maintained. In addition, the additional support of the synchronizing ring 26 can also reduce the amount of wear on the friction blocks (not illustrated), if such are located between the synchronizing ring 26 and the compressor housing 30, because it is not necessary for the friction blocks to provide a substantial portion of the synchronizer ring weight support. Further, when adjusting and calibrating the variable orifice assembly 20, the rigid coupling may also take the burden of centering the synchronizer ring 26 from the compressor housing 30.
    Still referring to FIG. 3, the shoulder portion 84 of the mounting bolt 58 can be generally configured such that when the lever arm 24 is rotatably attached to the mounting bolt 58, there is a gap 106 between the lever arm 24 and an adjacent surface 108 of the synchronizer ring 26 is created. Generally, the gap 106 may serve to allow any rotation of the lever arms 24 that may occur with respect to the mounting bolt 58 and / or the synchronizer ring 26. If e.g. a lever arm 24 is rotatably connected to the synchronizer ring 26 using a spherical bearing 61 mounted on the mounting bolt 58, the bearing 61 may allow the lever arm 24 to rotate both about the main axis 86 of the mounting bolt and about its longitudinal axis clockwise or counterclockwise rotate. Accordingly, the shoulder 84 may be generally configured to form a gap 106 that allows the lever arm 24 to rotate about the rotary motion interface 76 without touching or rubbing against the adjacent surface 108 of the synchronizer ring 26.
    In addition, the shoulder portion 84 may be further configured to be secured to the synchronizer ring 26 to provide additional means for attaching the mounting stud 58 to the synchronizer ring 26. For example, as shown in FIG. 3, the shoulder portion 84 may be welded to an adjacent surface 108 of the synchronizer ring 26 by at least a portion of the circumference of the shoulder portion. For example, the shoulder portion 84 may have a triangular, rectangular, pentagonal, hexagonal, or similar shape to define at least one planar edge to provide a suitable surface for welding the shoulder portion 84 to the synchronizer ring 26. In addition, when a groove 88 is defined between the lower segment 78 and the shoulder portion 84, the shoulder portion 84 may be disposed directly on and substantially in line with the adjacent surface 108 of the synchronizer ring 26. In that regard, an improved welded connection between the shoulder portion 84 and the ring 26 may be provided.
    Returning to Fig. 2, in one embodiment of the present subject matter, the lever arms 24 of the Verstellleitapparatanordnung 20 may be cantilevered. In that regard, the synchronizing ring 26 may be suspended suspended above the compressor housing 30. It should be understood that the distance 110 at which the synchronizer ring 26 is held away from the compressor housing 30 may generally vary depending on the configuration of the compressor 12 and / or the configuration of the variable area guide assembly 20. However, the spacing 110 may generally be selected so that the held synchronizer ring 26 does not rub against or otherwise contact the compressor housing 30 while the ring 26 is being rotated. Additionally, in one embodiment, one or more friction blocks (not illustrated) may be disposed along the outer circumference of the compressor housing 30 to provide a surface on which the suspended synchronizer ring 26 may slide during rotation of the ring 26 if necessary. In such an embodiment, as shown in FIG. 3, the mounting bolt 58 may be configured so that the lower segment 78, when secured to the synchronizer ring 26, does not project beyond a radially inner surface 112 of the ring 26. Accordingly, the fastening bolt 58 can be prevented from starting against some of the friction blocks and / or the compressor housing 30 when the ring 26 is rotated.
    In addition, the lever arms 24 may be flexible. Specifically, the lever arms 24 may be configured to flex or spring radially outward and / or radially outward, but support the synchronizer ring 26. Thus, the diameter of the synchronizing ring 26 and / or the height of the shaft segment 48 of the Verstellleitschaufel 22 may be selected in a particular embodiment of the present subject matter, that the connection point of the lever arm 24 is arranged radially outwardly to the mounting bolt 58 as the connection point of the lever arm 24th to the stem segment 48. Thus, as shown in FIG. 2, the lever arm may be bent or spring radially outwardly by a distance 114 between its first and second ends 66,68. Such bending or outward deflection ensures that the lever arms 24 are loaded radially inwards. Accordingly, when the synchronizer ring 26 is driven and the lever arms 24 change their orientation while pivoting, the lever arms 24 may continually apply an inwardly directed load on the synchroniser ring 26 to support its weight. This inward loading of the lever arms 24 may also provide a self-centering action on the synchronizer ring 26, thereby enabling more efficient alignment and adjustment of the variable area guide assembly 20. As also shown in FIG. 2, in one embodiment, the lever arms may also define a substantially tapered profile 116 along a portion of their length between the first and second ends 66,68. Such a tapered profile 116 can prevent the increase in tension within the lever arms 24 as the lever arms 24 rotate upon actuation of the synchronizer ring 26.
    It should be appreciated that although the variable orifice assembly 20 of the present invention has been described with respect to the variable orifices 22, the construction may also be utilized to provide a stage of variable inlet guide vanes of a compressor 12 or a stage of variable turbine vanes or vanes Turbine section 16 of a gas turbine 10 to drive. In addition, it should be readily apparent that the disclosed variable orifice assembly 20 can be used in an industrial gas turbine or adapted for use with any other suitable turbomachine known in the art, such as e.g. in propulsion-generating drive applications.
    A variable orifice assembly 20 for a compressor 12 having a plurality of variable vanes 22 is described. The Verstellleitapparatanordnung 20 has a synchronizing ring 26 and a plurality of fastening bolts 58 which are secured to the synchronizing ring 26. The Verstellleitapparatanordnung 20 has a plurality of lever arms 24, wherein each lever arm 24 has a first end 66 and a second end (68). The first end 66 of each lever arm 24 is attached to one of the Verstellleitschaufeln 22. In addition, a plurality of pivotal fasteners 60 are configured to connect the second end 68 of each lever arm 24 with a respective mounting bolt 58 to define a rotational interface 76 therebetween. Further, each of the mounting bolts 58 may be rigidly secured to a portion of each one of the pivot fasteners 60 such that there is substantially no additional radial or circumferential sliding relative movement between the synchronizer ring 26 and the plurality of lever arms 24 when the synchronizer ring 26 is rotated.
    LIST OF REFERENCE NUMBERS
    [0040]<Tb> 10 <September> Gas Turbine<Tb> 12 <September> compressor<Tb> 14 <September> combustion chambers<Tb> 16 <September> turbine section<Tb> 18 <September> wave<Tb> 20 <September> Verstellleitapparatanordnung<Tb> 22 <September> Verstellleitschaufeln<Tb> 24 <September> arm<Tb> 26 <September> synchronizer<Tb> 28 <September> actuator<Tb> 30 <September> compressor housing<Tb> 32 <September> vane segment<tb> 34 <SEP> First page or print page<Tb> 36 <September> Air<Tb> 40 <September> leading edge<Tb> 42 <September> trailing edge<tb> 44 <SEP> Inside top<tb> 46 <SEP> Outside foot<tb> 48 <SEP> One-piece stem segment<tb> 50 <SEP> Cylindrical opening<Tb> 52 <September> Bush<Tb> 54 <September> rotor blades<tb> 56 <SEP> Rotor disc or wheel<Tb> 58 <September> mounting bolts<Tb> 60 <September> rotary fastening device<Tb> 61 <September> Bearings<Tb> 62 <September> central axis<Tb> 64 <September> pushrod gear<tb> 66 <SEP> First end (from the lever arm 24)<tb> 68 <SEP> Second end (from the lever arm 24)<tb> 70 <SEP> Profiled seat<Tb> 72 <September> threaded pin<Tb> 74 <September> Mother<Tb> 76 <September> rotary motion interface<tb> 78 <SEP> Lower Section<tb> 80 <SEP> Middle section<tb> 82 <SEP> Upper section<Tb> 84 <September> shoulder portion<Tb> 86 <September> central axis<tb> 88 <SEP> Undercut grooves<tb> 90 <SEP> Lower extension<tb> 92 <SEP> Upper Extension<Tb> 94 <September> threaded hole<Tb> 96 <September> innerball<Tb> 98 <September> outer ring bore<Tb> 100 <September> hole<Tb> 102 <September> fastening device<tb> 104 <SEP> Radial outer surface<Tb> 106 <September> gap<tb> 108 <SEP> Adjacent area<Tb> 110 <September> distance<tb> 112 <SEP> Radial inner surface<Tb> 114 <September> distance<tb> 116 <SEP> Slender profile
    权利要求:
    Claims (8)
    [1]
    An adjustable nozzle assembly (20) for a compressor (12), wherein the variable nozzle assembly (20) comprises:a plurality of adjusting vanes (22); a synchronizer ring (26);a plurality of fastening bolts (58) secured to the synchronizing ring (26);a plurality of lever arms (24), each of the plurality of lever arms (24) having a first end (66) and a second end (68), wherein the first end (66) of each of the plurality of lever arms (24) on each of the plurality of Verstellleitschaufeln (22) is attached; anda plurality of pivotal fasteners (60), each of the plurality of pivotal fasteners (60) configured to connect a second end (68) of each one of the plurality of lever arms (24) to each of the plurality of fastener bolts (58) to provide a rotary motion interface (76 ) define,wherein each of the plurality of mounting bolts (58) are each rigidly connected to a component (96) of each of the plurality of pivotal fasteners (60) such that substantially no radial and circumferentially-oriented sliding movement is provided between the synchronizer ring (26) during rotation of the synchronizer ring (26). 26) and the lever arms (24) occurs.
    [2]
    The variable displacement guide assembly (20) of claim 1, wherein each of the plurality of pivotal fasteners (60) includes a bearing (61), each of the bearings (61) having an inner component (96) and an outer component (98) which is relative to the first inner component (96) is rotatable.
    [3]
    3. An adjusting guide assembly (20) according to claim 2, wherein the inner component (96) of each of the plurality of bearings (61) on each one of the plurality of fastening bolts (58) is rigidly fixed.
    [4]
    An adjuster assembly (20) according to claim 3, wherein the inner component (96) of each of the plurality of bearings (61) is rigidly secured to each one of the plurality of fastener bolts (58) by use of a threaded fastener (102).
    [5]
    5. The variable displacement guide assembly (20) of claim 1, wherein each of the plurality of lever arms (24) extends from a seat (70) disposed on a housing (30) of the compressor (12) cantilevered to the mounting bolt (58) such that the synchronizer ring (26) is at least partially supported about the housing (30) of the compressor (12).
    [6]
    6. Verstellleitapparatanordnung (20) according to claim 1, wherein each of the plurality of lever arms (24) between its first (66) and second end (68) is bent radially outward.
    [7]
    7. Verstellleitapparatanordnung (20) according to claim 1, wherein each of the plurality of lever arms (24) over at least a portion of its length has a tapered profile (116).
    [8]
    8. A compressor (12) for a gas turbine (10), wherein the compressor (12) comprises:a housing (30);a plurality of variable pitch vanes (22) disposed at least partially within the housing (20), each of the plurality of variable pitch vanes (22) having a shaft segment (48) extending through the housing (30); anda Verstellleitapparatanordnung (20) according to any one of the preceding claims.
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    同族专利:
    公开号 | 公开日
    DE102011053433A1|2012-03-29|
    CN102418712A|2012-04-18|
    US20120076641A1|2012-03-29|
    US8714916B2|2014-05-06|
    CH703871A2|2012-03-30|
    JP2012072763A|2012-04-12|
    JP5941259B2|2016-06-29|
    CN102418712B|2016-09-07|
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    法律状态:
    2017-03-15| NV| New agent|Representative=s name: GENERAL ELECTRIC TECHNOLOGY GMBH GLOBAL PATENT, CH |
    2021-04-30| PL| Patent ceased|
    优先权:
    申请号 | 申请日 | 专利标题
    US12/892,269|US8714916B2|2010-09-28|2010-09-28|Variable vane assembly for a turbine compressor|
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