阅读说明：本技术 改进的涡轮机转子组件 (Improved turbine rotor assembly ) 是由 S·S·布迪克 J·利格斯 于 2021-04-16 设计创作，主要内容包括：本发明题为“改进的涡轮机转子组件”。本发明公开了一种转子组件(300),该转子组件包括具有燕尾槽(36)的转子(34)。该燕尾槽(36)包括多个凹陷部(44)和第一径向最内表面(210)。转子叶片(20)包括从平台(31)径向向外延伸的翼型件(22)和从该平台(31)径向向内延伸的燕尾榫(32)。该燕尾榫(32)包括由该燕尾槽(36)的该多个凹陷部(44)接纳的在相反方向上延伸的多个突出部(40)。第二径向最内表面(46)限定从前缘表面(25)到后缘表面(27)的沟槽(33)。垫片(52)定位在该沟槽(33)内并且位于该燕尾槽(36)的该第一径向最内表面(210)和该燕尾榫(32)的该第二径向最内表面(46)之间。该垫片(52)至少部分地沿着该前缘表面(25)和该后缘表面(27)两者径向延伸,以在涡轮机的各种操作条件期间将该转子叶片(20)固定在该燕尾槽(36)内。(The invention provides an improved turbine rotor assembly. A rotor assembly (300) includes a rotor (34) having a dovetail slot (36). The dovetail slot (36) includes a plurality of recesses (44) and a first radially innermost surface (210). The rotor blade (20) includes an airfoil (22) extending radially outward from a platform (31) and a dovetail (32) extending radially inward from the platform (31). The dovetail (32) includes a plurality of protrusions (40) extending in opposite directions that are received by the plurality of recesses (44) of the dovetail slot (36). The second radially innermost surface (46) defines a groove (33) from the leading edge surface (25) to the trailing edge surface (27). A shim (52) is positioned within the groove (33) and between the first radially innermost surface (210) of the dovetail slot (36) and the second radially innermost surface (46) of the dovetail (32). The shim (52) extends radially at least partially along both the leading edge surface (25) and the trailing edge surface (27) to secure the rotor blade (20) within the dovetail slot (36) during various operating conditions of the turbine.)

1. A rotor assembly (300), comprising:

a rotor (34) having a dovetail slot (36), the dovetail slot (36) including a plurality of recesses (44) and a first radially innermost surface (210);

a gasket (52); and

a rotor blade (20) having a platform (31), an airfoil (22) extending radially outward from the platform (31), and a dovetail (32) extending radially inward from the platform (31), the dovetail (32) including a plurality of protrusions (40) extending in opposite directions received by the plurality of recesses (44) of the dovetail slot (36), the dovetail (32) including:

a leading edge surface (25);

a trailing edge surface (27);

a second radially innermost surface (46); and

a groove (33) defined along the second radially innermost surface (46) from the leading edge surface (25) to the trailing edge surface (27), wherein the shim (52) is positioned within the groove (33) and between the first radially innermost surface (210) and the second radially innermost surface (46), and wherein the shim (52) extends radially at least partially along both the leading edge surface (25) and the trailing edge surface (27).

2. The rotor assembly (300) of claim 1, wherein the shim (52) comprises: a first radially extending portion (304) extending along and contacting the leading edge surface (25); a second radially extending portion (306) extending along and contacting the trailing edge surface (27); and an axially extending portion disposed within the groove (33) and located between the first radially innermost surface (210) and the second radially innermost surface (46).

3. The rotor assembly (300) of claim 1, wherein a first corner (200) is defined at an intersection between the leading edge surface (25) and the second radially innermost surface (46), and a second corner (202) is defined at an intersection between the trailing surface and the second radially innermost surface (46), wherein the first corner (200) and the second corner (202) are arcuate.

4. The rotor assembly (300) of claim 3, wherein the first corner (200) is axially recessed relative to the leading edge surface (25) and the second corner (202) is axially recessed relative to the trailing edge surface (27).

5. The rotor assembly (300) of claim 4, wherein the shim (52) is positioned in contact with the first corner (200) and the second corner (202) such that the shim (52) is outside of a steam path.

6. The rotor assembly (300) of claim 3, wherein the shim (52) includes a radially outer surface (70) extending along and contacting the leading edge surface (25), the first corner (200), the groove (33), the second corner (202), and the trailing edge surface (27).

7. The rotor assembly (300) of claim 2, wherein the shim (52) includes a first radially inner surface (72) extending along the first radially innermost surface (210) of the dovetail slot (36) and a second radially inner surface (76) spaced apart from the first radially innermost surface (210) of the dovetail slot (36).

8. The rotor assembly (300) of claim 1, wherein the groove (33) comprises a radially defined depth within the dovetail (32), and wherein the depth varies from the leading edge surface (25) to the trailing edge surface (27).

9. The rotor assembly (300) of claim 1, wherein the groove (33) comprises a first depth at a leading edge face and a second depth at a trailing edge face, and wherein the groove (33) tapers from the first depth to the second depth along the second radially innermost surface (46).

10. A method of mounting a plurality of rotor blades (20) in a rotor assembly (300), the method comprising:

machining a first and second re-entrant angle onto a dovetail (32) of each rotor blade (20) of the plurality of rotor blades (20), wherein the first re-entrant angle is defined at an intersection between a leading edge surface (25) of the dovetail (32) and a radially innermost surface of the dovetail (32), and the second corner is defined at an intersection between a trailing edge surface (27) of the dovetail (32) and the radially innermost surface;

engaging the dovetail (32) of each rotor blade (20) into a corresponding dovetail slot (36) defined within a rotor (34), wherein a groove (33) is defined between the radially innermost surface of the dovetail (32) and the radially innermost surface of the dovetail slot (36);

inserting a shim (52) into a groove (33) until a first end of the shim (52) extends axially beyond the trailing edge face and a second end of the shim (52) extends axially beyond the leading edge face;

folding the first end of the shim (52) around the second re-entrant angle; and

folding the second end of the shim (52) around the first reentrant corner.

11. The method of claim 10, wherein the step of folding the first end of the shim (52) around the second re-entrant angle results in the first end of the shim (52) no longer extending axially beyond the trailing edge surface (27).

12. The method of claim 10, wherein the step of folding the second end of the shim (52) around the first reentrant corner results in the second end of the shim (52) no longer extending axially beyond the leading edge surface (25).

Technical Field

The present disclosure relates generally to turbomachines. In particular, the present disclosure relates to the support and/or retention of rotor blades in a turbomachine.

Background

Turbomachines, such as steam turbines, typically include a static nozzle assembly that directs a flow of working fluid into rotor blades connected to a rotating rotor. The nozzle configuration (including multiple nozzles or "airfoils") is sometimes referred to as a "diaphragm" or "nozzle assembly stage". Each rotor blade includes a base having a dovetail sized to fit within a corresponding dovetail slot in the rotor. Many last stage rotor blades have a significant length and have a significant weight. During low speed operation or "turning gear" operation, the blades are able to move within the dovetail slots in which they are retained. Such undesirable movement may cause severe wear to the blades and/or the rotor dovetail slots. In many cases, wear of the blades and dovetail slots can lead to disruptions, require repair, and result in undesirable costs.

However, during rotor assembly, some movement of the rotor blades ("unrolling") is required to facilitate assembly of the rotor blades. The rotor blades have outer cover ends and these ends typically have interlocking features. During row assembly, the rotor blades must pass each other. The rotor blades may also overlap the airfoil such that assembling the last rotor blade in the row may be difficult, if not impossible.

Accordingly, there is a need in the art for an improved system and method for rotor blade installation. In particular, there is a need for an improved system and method for rotor blade installation that allows for adequate clearance during assembly while maintaining proper containment of the rotor blades during turbine operation.

Disclosure of Invention

Aspects and advantages of the inventive rotor assembly, turbine, and method of mounting a plurality of rotor blades in a rotor assembly according to the present disclosure will be set forth in part in the description which follows, or may be obvious from the description, or may be learned by practice of the technology.

According to one embodiment, a rotor assembly is provided. The rotor assembly includes a rotor having a dovetail slot. The dovetail slot includes a plurality of recesses and a first radially innermost surface. The rotor assembly also includes a shim and a rotor blade having a platform. The airfoil extends radially outward from the platform and the dovetail extends radially inward from the platform. The dovetail includes a plurality of protrusions extending in opposite directions and received by a plurality of recesses of the dovetail slot. The dovetail also includes a leading edge surface, a trailing edge surface, and a second radially innermost surface. The dovetail also includes a groove defined along the second radially innermost surface from the leading edge surface to the trailing edge surface. The shim is positioned within the slot and between a first radially innermost surface of the dovetail slot and a second radially innermost surface of the dovetail. The shim extends radially at least partially along both the leading and trailing edge surfaces.

According to another embodiment, a turbine is provided. The turbomachine includes at least one turbine section, a rotor shaft extending axially through the at least one turbine section, and a rotor assembly coupled to the rotor shaft. The rotor assembly includes a rotor having a dovetail slot. The dovetail slot includes a plurality of recesses and a first radially innermost surface. The rotor assembly also includes a shim and a rotor blade having a platform. The airfoil extends radially outward from the platform and the dovetail extends radially inward from the platform. The dovetail includes a plurality of protrusions extending in opposite directions and received by a plurality of recesses of the dovetail slot. The dovetail includes a leading edge surface, a trailing edge surface, and a second radially innermost surface. The dovetail also includes a groove defined along the second radially innermost surface from the leading edge surface to the trailing edge surface. The shim is positioned within the slot and between a first radially innermost surface of the dovetail slot and a second radially innermost surface of the dovetail. The shim extends radially at least partially along both the leading and trailing edge surfaces.

In accordance with yet another embodiment, a method of installing a plurality of rotor blades in a rotor assembly is provided. The method includes machining a first and second re-entrant angle to a dovetail of each rotor blade of the plurality of rotor blades. The first fillet is defined at an intersection between a leading edge surface of the dovetail and a radially innermost surface of the dovetail. A second fillet is defined at an intersection between the trailing edge surface and the radially innermost surface of the dovetail. The method also includes engaging the dovetail of each rotor blade into a corresponding dovetail slot defined within the rotor. The slot is defined between a radially innermost surface of the dovetail and a radially innermost surface of the dovetail slot. The method further includes inserting the shim into the groove until a first end of the shim extends axially beyond the trailing edge face and a second end of the shim extends axially beyond the leading edge face. The method also includes folding around a first end of the second reentrant corner gasket and around a second end of the first reentrant corner gasket.

These and other features, aspects, and advantages of the rotor assembly, the turbine, and the method of mounting a plurality of rotor blades in the rotor assembly of the present invention will become better understood with reference to the following description and appended claims. The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments of the technology and together with the description, serve to explain the principles of the technology.

Drawings

A full and enabling disclosure of the rotor assembly, turbine, and method of installing a plurality of rotor blades in a rotor assembly, including the best mode of making and using the system and method of the present invention, directed to one of ordinary skill in the art, is set forth in the specification, which makes reference to the appended figures, in which:

FIG. 1 is a schematic illustration of a turbomachine in accordance with an embodiment of the present disclosure;

FIG. 2 illustrates a rotor blade according to an embodiment of the present disclosure;

FIG. 3 illustrates an enlarged perspective view of a rotor blade according to an embodiment of the present disclosure;

FIG. 4 illustrates an enlarged perspective view of a rotor blade dovetail according to an embodiment of the present disclosure;

FIG. 5 illustrates an enlarged perspective view of a rotor blade dovetail according to an embodiment of the present disclosure;

FIG. 6 illustrates an enlarged perspective view of a rotor showing a dovetail slot separated from a rotor blade dovetail according to an embodiment of the present disclosure;

FIG. 7 shows a perspective view of a shim according to an embodiment of the present disclosure;

FIG. 8 shows an enlarged perspective view of a shim according to an embodiment of the present disclosure;

FIG. 9 illustrates a cut-away view of a rotor blade engaged with a rotor according to an embodiment of the present disclosure;

FIG. 10 illustrates a radially outward facing perspective view of an axial retention member positioned relative to a rotor (excluding rotor blades) in accordance with an embodiment of the present disclosure;

FIG. 11 illustrates a blown-out perspective view of a rotor blade dovetail and shim according to an embodiment of the present disclosure;

FIG. 12 illustrates a blown-out perspective view of a rotor blade dovetail, shim, and cutaway rotor according to an embodiment of the present disclosure;

fig. 13 shows a simplified cross-sectional view of a trench according to an embodiment of the present disclosure;

FIG. 14 shows a cross-sectional view of a gasket according to an embodiment of the present disclosure;

fig. 15 illustrates a cross-sectional view of a rotor assembly according to an embodiment of the present disclosure;

fig. 16 illustrates a cross-sectional view of a rotor assembly according to an embodiment of the present disclosure; and is

Fig. 17 is a flow chart illustrating a method according to an embodiment of the present disclosure.

Detailed Description

Reference will now be made in detail to embodiments of the rotor assembly, turbine, and method of installing a plurality of rotor blades in a rotor assembly of the present invention, one or more examples of which are illustrated in the accompanying drawings. Each example is provided by way of explanation of the present technology, and not limitation of the present technology. In fact, it will be apparent to those skilled in the art that modifications and variations can be made in the present technology without departing from the scope or spirit of the claimed technology. For instance, features illustrated or described as part of one embodiment, can be used on another embodiment to yield a still further embodiment. Thus, it is intended that the present disclosure cover the modifications and variations of this invention provided they come within the scope of the appended claims and their equivalents.

Detailed description the detailed description uses numerical and letter designations to refer to features in the drawings. Like or similar designations in the drawings and description have been used to refer to like or similar parts of the invention. As used herein, the terms "first," "second," and "third" may be used interchangeably to distinguish one element from another and are not intended to denote the position or importance of the various elements.

As used herein, the terms "upstream" (or "upward") and "downstream" (or "downward") refer to relative directions with respect to fluid flow in a fluid pathway. For example, "upstream" refers to the direction from which the fluid flows, and "downstream" refers to the direction to which the fluid flows. The term "radially" refers to relative directions substantially perpendicular to an axial centerline of a particular component, the term "axially" refers to relative directions substantially parallel and/or coaxially aligned with the axial centerline of the particular component, and the term "circumferentially" refers to relative directions extending about the axial centerline of the particular component.

Approximate terms, such as "generally," "substantially," "approximately," or "about," include values within ten percent greater or less than the specified value. When used in the context of an angle or direction, such terms are included within ten degrees of greater or less than the angle or direction. For example, "generally vertical" includes directions within ten degrees of vertical in any direction (e.g., clockwise or counterclockwise).

Referring now to the drawings, FIG. 1 illustrates a schematic diagram of an exemplary opposed flow steam turbine 100. Although an exemplary steam turbine is shown and described herein, the present disclosure is not limited to this embodiment or steam turbine unless otherwise specified in the claims. For example, the invention as described herein may be used with any type of turbomachine, including but not limited to industrial or land-based gas turbines, aircraft gas turbines, or marine gas turbines. As shown in FIG. 1, the steam turbine 100 may define an axial direction A and a circumferential direction C extending about the axial direction A. The steam turbine 100 may also define a radial direction R that is perpendicular to the axial direction a.

As shown in FIG. 1, the steam turbine 100 may include a first Low Pressure (LP) section 105 and a second LP section 110. Each LP section 105 and 110 may include a plurality of diaphragm stages (not shown in FIG. 1). In one embodiment, each LP section 105 and 110 can include eight or more stages arranged adjacent to each other in the axial direction a. The last four stages or "edge stages" in the axial direction a are referred to as L0 stages, L1 stages, L2 stages, and L3 stages. The rotor blades of the L3 stage are smallest in the radial direction R, and the rotor blades in the remaining edge stages L2, L1 and L0 gradually increase in size in the radial direction R in steps in the axial direction a.

The L3 stage is the first stage in the edge stage in the axial direction a and is smallest in the radial direction R of the edge stage. The stage L2 is the penultimate stage and is the next stage in the axial direction a. The L1 stage is the penultimate stage of the four edge stages. The L0 stage is the last stage and is largest in the radial direction R. It should be understood that four stages are described as just one example, and that the LP sections 105 and 110 may have more or less than four edge stages.

The rotor shaft 115 may extend through the LP sections 105 and 110. Each LP section 105 and 110 may include a nozzle 120 and 125, respectively. A single shell or housing 130 may be divided along a horizontal plane and axially into an upper half section 135 and a lower half section 140, respectively. A single casing or shell 130 may span both LP sections 105 and 110. The central section 145 of the casing 130 includes a low pressure steam inlet 150. Within the outer shell or casing 130, the LP sections 105 and 110 are arranged in a single bearing span supported by journal bearings 155 and 160. The splitter 165 extends between the LP sections 105 and 110.

During operation, low pressure steam inlet 150 receives low pressure/intermediate temperature steam 170 from a source, such as, but not limited to, a High Pressure (HP) turbine or an Intermediate Pressure (IP) turbine, through a crossover conduit (not shown). Steam 170 is channeled through inlet 150, wherein splitter 165 splits the steam flow into two opposing flow paths 175 and 180. More specifically, in the exemplary embodiment, steam 170 is channeled through LP sections 105 and 110 wherein work is extracted from the steam to rotate rotor shaft 115. The steam exits LP sections 105 and 110, where it is channeled for further processing (e.g., to a condenser).

It should be noted that, as will be understood by those of ordinary skill in the art, although FIG. 1 illustrates a counter-flow low-pressure turbine, the systems and methods of the present disclosure are not limited to use with only an LP turbine, but may be used with any counter-flow turbine, including, but not limited to, an IP turbine and/or an HP turbine. Further, the systems and methods of the present disclosure are not limited to use with only opposed-flow turbines, but may also be used with other turbine types (e.g., uniflow steam turbines).

FIG. 2 illustrates a schematic perspective view of a steam turbine rotor blade 20 (e.g., within an L1 stage or an L0 stage) according to various embodiments of the present disclosure. As shown, the steam turbine rotor blade 20 may include a blade or airfoil 22 having a leading edge 35, a trailing edge 37, a radially outer first end 24, and a radially inner second end 26 opposite the first end 24. The first end 24 of the airfoil 22 may include a tip 28, which may be coupled to a shroud (not shown) in some embodiments. At the second end 26 of the airfoil 22 is a base 30 that includes a dovetail 32 for engaging and complementing a corresponding dovetail slot 36 (FIG. 6) in a rotor 34.

The rotor blade 20 may also include a platform 31 that generally surrounds the dovetail 32 and the airfoil 22. An exemplary platform may be positioned at an intersection or transition between the airfoil 22 and the dovetail 32, and may extend outwardly in generally axial and tangential directions, as shown. In various embodiments, the airfoil 22 may extend radially outward from the platform 31 and the dovetail 32 may extend radially inward from the platform 31. In many embodiments, the platform 31 generally serves as a radially inward flow boundary for the working fluid flowing through the vapor path.

As shown in FIG. 2, a groove or tapered groove 33 may extend along a radially inner portion of the dovetail 32. The dovetail 32 may extend between a leading edge face 25 radially inward from the leading edge 35 and a trailing edge face 27 radially inward from the trailing edge 37. Trailing edge face 27 may include retention features 54, as discussed further herein.

In some embodiments, tapered slot 33 may be deeper near leading edge face 25 (i.e., extend radially deeper into the dovetail), and the depth of slot 33 gradually decreases as it extends along dovetail 32 to trailing edge face 27. As one non-limiting example, the depth of tapered groove 33 near leading edge face 25 may be about 0.30 inches, and the depth of groove 33 near trailing edge face 27 may be about 0.12 inches. In other embodiments, the depth of tapered groove 33 near leading edge face 25 may be between about 0.20 inches and about 0.40 inches. Also, in some embodiments, the depth of the groove 33 near the trailing edge face may be between about 0.08 inches and about 0.16 inches.

FIG. 3 illustrates an enlarged perspective view of a portion of the steam turbine rotor blade 20. As shown, the dovetail 32 may include a body 38, a plurality of tabs 40 extending in opposite directions from the body 38, a radially innermost surface 46, and a tapered groove 33 extending along the length of the dovetail 32 within the radially innermost surface 46. The plurality of projections 40 are sized to complement a plurality of recesses 44 in a corresponding dovetail slot 36 (FIG. 12). In various embodiments, the tapered groove 33 opens at the radially innermost surface 46 and is sized to engage a shim 52 (fig. 7, in the manner shown in fig. 12). The tapered groove 33 extends along the entire radially innermost surface 46 of the body 38. In various embodiments, the body 38 includes a bulbous section 48 for complementing one of the plurality of recesses 44 in the dovetail slot 36.

FIG. 4 illustrates an enlarged perspective view of the leading edge surface 25 of the dovetail 32 according to an embodiment of the present disclosure. Similarly, FIG. 5 shows an enlarged perspective view of the trailing edge surface 27. As shown, the dovetail 32 may also include a first corner 200 defined at the intersection between the leading edge surface 25 and the radially innermost surface 46 of the dovetail 32. Likewise, a second corner 202 may be defined at the intersection between the rear surface 27 and the radially innermost surface 46. As shown in fig. 4 and 5, the first and second corners 200, 202 may be arcuate and/or substantially smoothly curved. In many embodiments, the first and second corners 200, 202 may serve, at least in part, to provide a smooth surface to turn the end of the shim 52 around without causing the shim 52 to crack and/or break.

As shown in fig. 4, in some embodiments, the first corner 200 and/or the second corner 202 may include an axial depression 204 relative to the leading edge surface 25. Specifically, the axial recess 204 may include an axially extending portion 206 and a radially extending portion 208 that intersect one another. Specifically, the axially extending portion 206 may be generally perpendicular to the leading edge surface 25 and may extend between the leading edge surface 25 and the radially extending portion 208. The radially extending portion 208 may be generally parallel to the leading edge face 25 and may extend between the axially extending portion 206 and the first corner 200 and/or the radially innermost surface 46. The radially extending portion 208 of the axial recess 204 may be disposed axially inward from the leading edge surface 25. Although not shown in FIG. 5, in many embodiments, the second corner 202 may also include an axial recess 204 relative to the trailing edge surface 27.

FIG. 6 illustrates a rotor 34 (e.g., a steam turbine rotor) including a plurality of dovetail slots 36 for coupling with the dovetails 32 of the rotor blades 20. Each dovetail slot 36 of the plurality of dovetail slots 36 includes a plurality of recesses 44 that may be sized to receive a plurality of protrusions 40 extending from each dovetail 32. Additionally, as shown in FIG. 6, each dovetail slot 36 may include a radially innermost surface 210. When the dovetail 32 is installed in the dovetail slot 36, the radially innermost surface 210 of the dovetail slot 36 may contact either or both of the radially innermost surface 46 of the dovetail 32 and/or the shim 52.

Fig. 7 and 8 show the shim 52 in more detail. In various embodiments, the shims 52 may be sized to engage the tapered grooves 33 in the rotor blade 20 and to retain the rotor blade 20 within the dovetail slots 36. In many embodiments, the shim 52 may include a body 68 having a first thickness (t) measured between an upper or radially outer surface 70 and a lower or first radially inner surface 72 of the body 68₁). The thinned region 74 can extend from one end of the body 68 (e.g., the thicker end of the shim 52) and can be included in the radially outer surface 70 (which is the radially outer surface)Continuous between the body 68 and the thinned region 74) and a thinned or second radially inner surface 76 (t)₂)。

In some embodiments, the second thickness (t)₂) Between the first thickness (t)₁) Between about 5% and about 70%. In other embodiments, the second thickness (t)₂) Between the first thickness (t)₁) Between about 15% and about 60%. In many embodiments, the second thickness (t)₂) Between the first thickness (t)₁) Between about 25% and about 50%. In various embodiments, the second thickness (t)₂) Between the first thickness (t)₁) Between about 35% and about 45%. Connecting the body 68 and the thinned region 74 is a first tapered region 78 that tapers outwardly from the body 68 to the thinned region 74. In various embodiments, the length (l) of thinned region 74_TR) May be equal to the length (l) of the body 68_MB) Approximately one quarter of the length of the body 68, or one eighth of the length of the body 68, or three sixteenths of the length of the body 68, or between about 10% and about 25% of the length of the body 68.

In many embodiments, when the shim 52 is installed between the rotor 34 and the rotor blade 20, the radially outer surface 70 may be in contact with the rotor blade 20, and the first radially inner surface 72 may be in contact with the rotor 34 to advantageously retain the rotor blade 20 within the dovetail slot 36. It should be understood that the shims 52 may be inserted into the tapered grooves 33 in either a forward or rearward direction, depending on the clearance and desired mounting technique.

As described herein, the shim 52 is configured to fit within the tapered slot 33 and between the dovetail 32 of the rotor blade 20 and the dovetail slot 36 of the rotor 34, and to help retain the rotor blade 20 within the rotor 34. Moreover, in various embodiments, thinned region 74 improves the ease of installing and removing shims 52 within the tight clearances of the steam turbine. That is, thinned region 74 may allow for flexing of shim 52 or folding over of the ends of shim 52 to lock the shim to rotor 34, for example, folding over the ends of shim 52 over first corner 200 and second corner 202 (fig. 4 and 5).

The thinned region 74 is preferably located on the thicker end of the shim 52, as the thicker end will be more difficult to fold than the opposite thinner end. Region 74 is thinned to ensure a proper turndown to thickness ratio so that cold working does not result in cracking or high residual stress regions. The reduced thickness facilitates the folding of a portion of the shim 52 to lock it to the rotor 34, and the opposite end near the thin end may also be folded in a similar manner to lock the shim 52 to the rotor 34.

One important reason for the need for the turn at the thick end is that during operation, the radial gap between the rotor dovetail base 210 and the bucket dovetail base 46 may increase due to mechanical growth. This radial gap will allow the wedges or shims to move toward the thin end during operation, and then during shutdown, the radial gap will return to normal height. Since the wedges/shims may have moved forward and filled the larger gaps, there will be no room for the blade to return to the unstressed state during shutdown. The filled radial gap will result in over-compression of the wedges/shims such that the stress may exceed yielding and/or disassembly of the wedges and it is almost impossible to remove the wedges/shims due to the extremely high compressive loads.

FIG. 9 illustrates a cut-away view of rotor blade 20 engaged with rotor 34 and a portion of axial retention member 64 for axially retaining rotor blade 20 within space 66 within rotor 34. As shown in FIG. 9, the rotor blade 20 may also include axial retention features 54 extending from a side 56 of the body 38. In many embodiments, the side 56 may be the leading edge surface 25, the trailing edge surface 27, or both. However, in the embodiment shown in FIG. 9, the axial retention feature extends from the trailing edge surface 27. In many embodiments, the axial retention feature 54 may include a hook 58 having a first member 60 extending generally perpendicularly from the trailing face 27 and a second member 62 extending from the first member 60 generally parallel to the trailing face 27. As further described herein, the axial retention features 54 may be used to provide a space into which the axial retention members 64 may fit to axially retain the dovetail 32 within the dovetail slot 36. In various embodiments, the axial retention feature 54 defines a space 66 between the second member 62 and the trailing face 27 that is sized to engage the axial retention member 64.

FIG. 10 shows a radially outward facing perspective view of the axial retention member 64 positioned relative to the rotor 34 (excluding the blades 20). In some cases, the axial retention member 64 also includes an anti-rotation tab 65 for engaging the hook 58 (fig. 9) and for preventing the axial retention member 64 from rotating within the space 66 (fig. 9). Additionally, an anti-rotation pin 67 may be coupled to the rotor 34 to prevent radial movement of the axial retaining member 64 within the space 66.

Fig. 11 and 12 show blown-out perspective views of rotor blade 20, rotor 34 and spacer 52. As shown in FIG. 11, the tapered slot 33 is disposed along a radially innermost surface 46 of the dovetail 32 of the rotor blade 20, which is disposed opposite a radially innermost surface 210 within the dovetail slot 36 of the rotor 34. Likewise, the shim 52 may be sized to fit within the tapered slot 33 of the dovetail 32 to space the radially innermost surface 210 of the dovetail slot 36 and the radially innermost surface 46 of the dovetail 32 apart such that the rotor blade 20 is properly constrained within the rotor 34 during various operations of the steam turbine 100.

In many embodiments, the shim 52 is used to provide a rigid solution for locking the dovetail 32 of the rotor blade 20 into the dovetail slot 36 of the rotor 34. Moreover, in various embodiments, the shim 52 may be rigid such that it retains the rotor blade 20 within the rotor 34 without buckling, flexing, buckling, or moving during operation of the steam turbine. In this manner, the shim 52 may be advantageous over other flexible devices that retain the rotor blade 20 within the rotor 34 because it does not kink, flex, or move during operation of the steam turbine 100.

As described herein, the rotor blade 20 may be an L1 stage rotor blade 20 and/or an L0 stage rotor blade 20, meaning that the rotor blade 20 may be much larger and heavier when compared to rotor blades in the L2 and L3 stages. For example, the L0 and/or L1 stage rotor blades 20 may be between about 20 inches and about 30 inches in length and may have a weight in excess of 20 pounds. In some embodiments, the L0 and/or L1 stage rotor blades 20 may have a weight in excess of 100 pounds. In other embodiments, the L0 and/or L1 stage rotor blades 20 may have a weight in excess of 200 pounds. Thus, a relatively large L0 and/or L1 stage rotor blade 20 will impart a much greater torque to the dovetail slot 36 of the rotor 34 when compared to the L2 and/or L3 stages. Thus, a resilient retention solution (such as a spring) that can successfully retain the smaller L2 and/or L3 stage rotor blades cannot accommodate the relatively larger and heavier L0 and/or L1 stage rotor blades 20 due to their size and weight. Accordingly, a robust and rigid retention solution (such as the shim 52 shown and described herein) is needed to accommodate large L0 and/or L1 rotor blades 20.

Fig. 13 shows a simplified cross-sectional view of a tapered trench 33 according to various embodiments. As shown, the tapered trench 33 may include a flat portion 1101 near the leading edge surface 25 and/or the trailing edge surface 27, where the flat portion 1101 has a constant depth (i.e., it is not tapered). The depth 1102 of the tapered groove 33 at the deep end (left side of fig. 13) is greater than the depth 1103 (and depth 1104) near the opposite end (right side of fig. 13).

The flat section 1101 has a constant depth 1104 throughout its length. In some embodiments, the length of the flat section 1101 may be about 3% to about 20% of the entire length of the tapered groove 33. In other embodiments, the length of the flat section 1101 may be about 5% to about 18% of the entire length of the tapered groove 33. In various embodiments, the length of the flat section 1101 may be about 7% to about 15% of the entire length of the tapered groove 33. In many embodiments, the length of the flat section 1101 may be about 9% to about 13% of the entire length of the tapered groove 33.

The flat section 1101 facilitates removal of the shim 52 after turbine operation, and may also be removed in the field without the use of a cutting tool. The flat section 1101 allows for a larger gap at the thin end of the wedge. The gap may bend the thin end back to nearly straight and then be able to tap the wedge toward the thick end. Without this additional clearance region, the end return bends would form a "mushroom" folded region and would not allow the thin end to easily disengage. In addition, the flat section 1101 becomes a third level datum for machining and inspection of the blade, as the use of trench taper would not be prudent or robust.

Fig. 14 shows a simplified cross-sectional view of the shim 52. The shim 52 includes a thick end 77 and an opposite thin end 75, with the overall thickness gradually transitioning between the opposite ends. Thinned region 74 is a reduced thickness region that enables shim 52 to be folded over corners 200, 202 to lock shim 52 in place. This is particularly effective when both ends of the shim are turned over the corners 200, 202, as the shim is prevented from moving in the axial direction (relative to the turbine). For example, a first end 75 of the shim 52 may have a first thickness 1202 and an opposite second end 77 of the shim may have a second thickness 1201, wherein the second thickness 1201 is greater than the first thickness 1202. The intermediate height of shim 52 gradually transitions from first height 1202 to second height 1201.

As shown and described herein, the shim 52 may be tapered to closely match the dimensions of the tapered channel 33 such that the shim is securely received and contained within the tapered channel 33. Accordingly, the spacer 52 may be tapered to allow the spacer 52 to be easily inserted into the tapered groove 33. Thus, the tapered shim 52 may be advantageous over other types of shims (e.g., flat shims) because it is easily inserted into the tapered groove 33. For example, it may be difficult or impossible to insert flat shims due to the tight tolerances and substantial weight of the LO and/or L1 rotor blades 20. Accordingly, tapered shims, such as tapered shim 52 shown and described herein, may be advantageous.

In many embodiments, the spacer thinned region 74 can extend from the second (thicker) end 77 to the first tapered region 78. The first tapered region 78 may transition the shim 52 from the thinned region 74 to the body 68. In various embodiments, as shown, the thickness of the shim 52 may increase from the thinned region 74 to the body 68. In many embodiments, the thickness of the body 68 of the gasket may then taper from the first tapered region 78 to the first (thinner) end 75.

Fig. 15 illustrates a rotor assembly 300 according to an embodiment of the present disclosure. As shown in fig. 15, the shim 52 may be mounted in a tapered groove 33 (not shown for clarity) and the ends of the shim 52 may be turned over the corners 200, 202. With both ends of the shim 52 folded over (as shown), the shim 52 is prevented from moving axially relative to the wheel/rotor 34 (i.e., to the left or right in fig. 15). The curved and/or arcuate corners 200, 202 may advantageously reduce cold work stresses on the shim 52 when the ends are turned during installation.

As shown in FIG. 15, the dovetail 32 may include a leading edge surface 25, a trailing edge surface 27, and a radially innermost surface 46 extending therebetween. In many embodiments, the shim 52 may be positioned within the slot 33 (not shown) and between the radially innermost surface 46 of the dovetail 32 and the radially innermost surface 210 of the dovetail slot 36. As shown in fig. 15, the shim 52 may extend radially at least partially along both the leading and trailing edge surfaces 25, 27. In many embodiments, as shown, the shim 52 may include a first radially extending portion 304 that extends along and contacts the leading edge surface 25, and a second radially extending portion 306 that extends along and contacts the trailing edge surface 27. The axially extending portion 308 may be disposed within the groove 33 and positioned between the radially innermost surface 46 of the dovetail 32 and the radially innermost surface 210 of the dovetail slot 36 of the rotor 34.

In various embodiments, first radially extending portion 304, second radially extending portion 306, and axially extending portion 308 may extend continuously between one another. For example, the first radially extending portion 304 of the shim 52 may transition to the axially extending portion 308 of the shim 52 at the first curved portion 305. Similarly, the second radially extending portion 306 of the shim 52 may transition to an axially extending portion 308 of the shim 52 at a second curved portion 307. As shown in fig. 15, the first curved portion 305 of the shim 52 may be disposed between the first radially extending portion 304 and the axially extending portion 308. In many embodiments, the first curved portion 305 of the shim 52 may extend along and contact a first corner 200 disposed between the leading edge surface 25 and the radially innermost surface 46 of the dovetail 32.

Likewise, the second curved portion 307 of the shim 52 may be disposed between the second radially extending portion 306 and the axially extending portion 308 of the shim 52. Additionally, a second curved portion 307 may extend along and contact a second corner 202 disposed between the trailing edge surface 27 and the radially innermost surface 46 of the dovetail 52. As shown and described herein, the first and second radially extending portions 304, 306 and the first and second curved portions 305, 307 of the shim 52 may be used to advantageously provide axial retention of the dovetail 32 within the rotor 34.

As shown in FIG. 15, a first corner 200 of the dovetail 32 may be defined at the intersection between the leading edge surface 25 and the radially innermost surface 46 of the dovetail 32. Likewise, a second corner 202 of the dovetail 32 may be defined at the intersection between the trailing edge surface 27 and the radially innermost surface 46 of the dovetail 32. As shown, the first and second corners 200, 202 may be curved, arcuate, and/or substantially smooth surfaces positioned between the generally radially-oriented leading and trailing edge surfaces 25, 27 of the dovetail 32 and the generally axially-oriented radially-innermost surface 46.

The first and second corners 200 may be used to provide a smooth surface for the ends of the shim 52 to bend around during installation without cracking. The size of the radius of the corners 200, 202 is important because, for example, if the radius of the corners is too small (the bend is too small and the angle is too sharp), the ends of the shim 52 may crack and/or break when folded over the corners 200, 202 during installation of the shim 52. Thus, advantageously, the radius of the corners 200, 202 is at least 150% of the thickness of the shim 52 at its ends. For example, in many embodiments, the radius of the corners 200, 202 may be between about 150% and about 300% of the thickness of the shim 52 at its ends 75, 77. In other embodiments, the radius of the corners 200, 202 may be between about 175% and about 275% of the thickness of the shim 52 at its ends 75, 77. In various embodiments, the radius of the corners 200, 202 may be between about 200% and about 250% of the thickness of the shim 52 at its ends 75, 77. In particular embodiments, the radius of the corners 200, 202 may be about 225% of the thickness of the shim 52 at its ends 75, 77.

It may be advantageous to machine the first and second corners 200, 202 onto the dovetail 32, as shown, rather than, for example, onto the rotor 34, for a variety of reasons. Specifically, machining the first and second corners 200, 202 onto the dovetail 32 rather than the rotor may have fewer associated risks and be more cost effective. For example, machining the corners 200, 202 onto the rotor 34 may be difficult due to the complex shape of the rotor 34, which may result in undesirable stress risers within the rotor 34 and, if mishandled, may result in the scrapping of a relatively expensive rotor 34. However, due to the geometry and dimensions of the unitary rotor blade 20, it is much easier to machine the corners 200, 202 onto the dovetail 32 of the rotor blade 20, as compared to the rotor 34. Moreover, machining the corners 200, 202 onto the dovetail 32 has fewer associated risks as compared to the rotor 34, because the rotor blade 20 is a less expensive part to produce. Thus, if an error occurs during machining of the corners 200, 202, replacing a single rotor blade 20 will be more cost effective than replacing the entire rotor 34.

As shown in fig. 14 and 15, the shim 52 may also include a radially outer surface 70, a first radially inner surface 72, and a second radially inner surface 76. As shown, radially outer surface 70 may extend continuously along and contact leading, first corner, groove, second corner, and trailing surface 25, 200, groove 33, 202, and 27 without any contact gaps or spaces. It is advantageous that the radially outer surface 70 of the shim 52 have as much contact as possible with the radially innermost surface 46 of the dovetail 32 in order to maintain retention of the shim 52 during operation of the steam turbine 32. The first radially inner surface 72 may be spaced apart from the radially outer surface 70 and may extend along a radially innermost surface 210 of the dovetail slot 36. The second radially inner surface 76 may be spaced apart from the radially outer surface 70 and a radially innermost surface 210 of the dovetail slot 36 of the rotor 34. As shown, the second radially inner surface 76 may not be in contact with any other surface, i.e., it may be exposed to ambient air.

Fig. 16 illustrates another rotor assembly 300 according to an embodiment of the present disclosure. As shown, the rotor assembly 300 may also include a first axial recess 204 relative to the leading edge surface 25 and a second axial recess 205 relative to the trailing edge surface 27. In particular, each of the axial recesses 204, 205 may include an axially extending portion 206, 207 and a radially extending portion 208, 209 that intersect one another. Specifically, the axially extending portion 206 on the leading edge side may be generally perpendicular to the leading edge surface 25 and may extend between the leading edge surface 25 and the radially extending portion 208. The radially extending portion 208 may be generally parallel to the leading edge surface 25 and may extend between the axially extending portion 206 and the first corner 200 and/or the radially innermost surface 46. Similarly, the axially extending portion 207 of the second axial recess 205 may be generally perpendicular to the trailing edge surface 27 and may extend between the trailing edge surface 27 and the radially extending portion 209. The radially extending portion 209 of the second axial recess 205 may be generally parallel to the trailing edge surface 27 and may extend between the axially extending portion 207 and the second corner 202 and/or the radially innermost surface 46.

The radially extending portions 208, 209 of the axial recesses 204, 205 may be axially spaced from the leading or trailing edge surfaces 25, 27 to provide pockets that protect the ends of the shim 52 from corrosion caused by the steam path 302. In this manner, the portions of the gasket 52 extending along the corners 200, 202 may be advantageously positioned outside of or away from the steam path 302 in order to extend the life of the gasket 52 and prevent end corrosion. Undesirable corrosion of the ends of the shim 52 may cause the shim 52 to recede (i.e., dislodge) from the groove 33 during operation of the steam turbine 100. Accordingly, the axial recesses 204, 205 advantageously provide a protective pocket for the radially extending portions 304, 306 and the curved portions 305, 307 spaced from the steam path 302 to prevent undesired corrosion.

FIG. 17 provides a flow chart that diagrammatically illustrates an example method 400 of installing a plurality of rotor blades (such as rotor blade 20 and rotor 34 described herein) within a rotor according to one or more example embodiments of the present disclosure. As shown in FIG. 17, method 400 may include a step 402 of machining first and second fillets 200, 202 onto dovetails 32 of each rotor blade 20 of the plurality of rotor blades 20. The first fillet 200 may be defined at an intersection between the leading edge surface 25 of the dovetail 32 and the radially innermost surface 46 of the dovetail 32. The second fillet 202 may be defined at an intersection between the trailing edge surface 27 of the dovetail 32 and the radially innermost surface 46 of the dovetail 32.

In many embodiments, the method 400 may further include the step 404 of engaging the dovetail 32 of each rotor blade 20 into a corresponding dovetail slot 36 defined within the rotor 34. The groove 33 may be defined between the radially innermost surface 46 of the dovetail 32 and the radially innermost surface 210 of the dovetail slot 36. In various embodiments, the method 400 may further include the step 406 of inserting the shim 52 into the groove 33 until the first end 75 of the shim 52 extends axially beyond the trailing edge surface 27 and the second end 77 of the shim 52 extends axially beyond the leading edge surface 25. In many embodiments, the method 400 may further include the step 408 of folding the first end 75 of the gasket around the second reentrant corner 202. In some embodiments, the method 400 may include the step 410 of folding the second end 77 of the shim 52 around the first reentrant corner 200. In some embodiments, step 406 occurs before either or both of steps 408 and 410 in order to ensure that the shim is fully inserted into the groove 33. The order of steps 408 and 410 may be reversed.

This written description uses examples to disclose the invention, including the best mode, and also to enable any person skilled in the art to practice the invention, including making and using any devices or systems and performing any incorporated methods. The patentable scope of the invention is defined by the claims, and may include other examples that occur to those skilled in the art. Such other examples are intended to be within the scope of the claims if they include structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal languages of the claims.