TURBINE REAR STRUCTURES, CORRESPONDING GAS TURBINE ENGINE, AIRCRAFT AND METHOD OF MANUFACTURING

Technical Field The present invention is concerned with an improved gas turbine structure and specifically, but not exclusively, to a turbine rear structure (TRS).

In a gas turbine engine of the type used in commercial aircraft a gas turbine generates the thrust for the aircraft. Air is received at the front of the engine, compressed and mixed with fuel before being ignited generating a flow of high speed exhaust gases. Because of the continuous rotation of the blades within the engine the gases similarly swirl or circulate around the axis of the engine. On exiting the engine it is advantageous to compensate for this swirl so as to direct gases out of the rear of the engine in a direction opposite to that of flight.

This maximises the thrust that is generated since the gas flows in a direction parallel with the axis of the engine.

In order to change the direction of flow (i.e. to turn the exhaust gas flow) the rear section of the engine (after the turbine) contains a row of static outlet guide vanes that are arranged so as to turn the exhaust gas from a circulating or swirling direction of flow into a substantially axial direction of flow out of the rear of the engine. Such vanes are commonly used to increase the thrust from the engine. However, there is a limit to how much the vanes can be contoured to turn the exhaust gas. Too great an angle and the exhaust gas is inhibited from leaving the engine at high speed. In effect the vanes become a restriction in the exhaust gas path. There is therefore a tradeoff or balance in engine design between optimising the thrust generated from the exhaust gas against inhibiting the exhaust gas flow from the engine.

As engines become more and more powerful (i.e. increasing the power output from the turbine) the exhaust gases have ever increasing components of circular flow (or swirl) and this causes reductions in efficiencies at the exhaust of the engine where all of the circular flow component (swirl) cannot be changed without limiting the exhaust gas flow. The matter is further complicated by separation of exhaust gas occurring at the surfaces of the turning vanes. Separation means that exhaust gas is not turned according to the profile of the vanes but instead detaches from the surface further limiting the amount of de-swirling (i.e. the removal of the exhaust gas rotational velocity component) in a conventional engine design.

The present inventor has established an alternative way to allow for increased engine power and exhaust gas flow whilst still allowing for the effective re-direction of the exhaust gas from the rear of the engine. The inventor has furthermore established a way to do this without increasing the size or length of the rear section of the engine.

Summary of the Invention

Aspects of the invention are set out in the accompanying claims. Viewed from a first aspect there is provided a turbine rear structure for a gas turbine engine, the structure comprising a central hub and a circumferential outer ring, the structure further comprising a first group of guide vanes extending between the hub and ring and a second group of guide vanes located between adjacent vanes of said first group, and wherein the second group of guide vanes are located asymmetrically with respect to adjacent vanes of said first group.

The second group of vanes are termed 'splitter vanes' or 'intermediate vanes' throughout this description. In effect, the second group of splitter vanes divide the spaces between adjacent vanes in the first group into two separate flows through the TRS. Exhaust gas flows on either side of each of the splitter vanes.

Each of the vanes in the first group of vanes is configured to cause exhaust gas passing over the respect vane to change direction i.e. the vanes each have an aerodynamic profile or shape which is designed to cause exhaust gas entering the TRS to leave the TRS with a reduced component of swirl. This is achieved by providing each vane with a smooth aerodynamic shape.

The second group of splitter vanes substantially enhances the way in which the exhaust gas direction can be changed through the TRS. Put another way the splitter vanes improve the de-swirling effect through the TRS.

The splitter vanes also have an aerodynamic profile to effect turning and de-swirling and have a shape that generally complements the operation of the first group of vanes. As well as an aerodynamic profile the splitter vanes may be specifically positioned between adjacent vanes in the first group.

For example adjacent vanes of said first group may comprise an upstream vane in an exhaust gas direction and wherein the second group of vanes are positioned closer to an upstream vane than a downstream vane of said first group. The term upstream is intended to refer to a vane against which the exhaust gas first strikes the leading edges of the vane. For example if the swirl is in a clockwise direction the exhaust gas will impinge on successive vanes in a clockwise direction. Here, the splitter vanes may be located closer to the vane against which the exhaust gas impinges first.

The second group of vanes may be positioned approximately 1/3rd of the distance plus or minus 1/6th of the distance across the space defined between adjacent vanes of said first group measured from an upstream vane of said first group.

The distance is measured around the circumference of a circle extending between the vanes rather than a straight line between adjacent vanes.

The second group may alternatively be positioned approximately 1/3rd of the distance across the space defined between adjacent vanes of said first group measured from an upstream vane of said first group. The inventor has established that placing the splitter vanes at this position optimises the turning effect of the TRS.

One or more of the first group of vanes may be load bearing vanes connecting the hub and circumferential ring. These are in effect conventional vanes of a TRS and provide the load bearing path between the hub and ring. Additionally, one or more of the second group of vanes may also be load bearing vanes connecting the hub and circumferential ring or may be non-load bearing vanes i.e. their function is purely aerodynamic.

The second group of vanes may extend across the whole distance between the hub and ring. Alternatively, the second group of vanes may extend a predetermined distance from the hub. Thus, the second group of vanes may only be coupled at a first end to the hub and have an opposing radially extending end terminating a predetermined radius from the hub. Advantageously this prevents any thermally induced loading on the vane since the vane is permitted to expand within the TRS.

The second group of vanes may additionally extend in an axial direction of the structure to a distance between 20 and 100% of the full chord-length of the first group of vanes measured from a leading edge of the first group of vanes. Thus, the splitter vanes may be shorter and smaller than the first group of vanes which may be load bearing.

The second group of vanes may be arranged so that their leading edges align with the leading edges of the vanes in the first group. Alternatively, a leading edge of the second group of vanes may be displaced in an axial direction of the structure so that the leading edge of the second group of vanes is downstream of the leading edge of the first group of vanes in an exhaust gas flow direction.

Alternatively, a leading edge of the second group of vanes may be displaced in an axial direction of the structure so that the leading edge of the second group of vanes is upstream of the leading edge of the first group of vanes in an exhaust gas flow direction. In effect the second group of vanes may extend beyond a plane defined by the leading edges of the first set of vanes.

Thus, depending on the engine characteristics the turning effect of the splitter vanes may be fully optimised. Furthermore, alternating splitter vanes around the circumference of the TRS may alternate between the two displacements adding a further dimension to optimisation i.e. adjacent vanes alternating between an upstream and a downstream position.

Because of the aerodynamic shape of the vanes in the first group of vanes required to turn the exhaust gas each vane comprises one side with a convex shape and an opposing side with a concave shape. As high speed exhaust gas passes over the surface of the convex side there is a tendency or possibility for the gas flow to separate from the convex surface. Thus, an outer convex surface of each of said first group of vanes has a region of maximum negative pressure at a portion of its surface. Advantageously each of said second group of vanes may be arranged to overlap said region of maximum negative pressure. The inventor has established that overlapping a splitter vane over the point or region of maximum negative pressure (termed a suction peak herein) prevents or helps avoid separation of the exhaust gas flow from the vane. This further optimises the gas turning effect. The inventor has also established an optimal range of location for the splitter vane with respect to this suction peak region or zone.

Each of said second group of vanes has a chord length h. Advantageously the leading edge of each of said second group of vanes may be displaced axially from the region of maximum negative pressure by a distance of 25% of the chord length (h) +/- 15% of the chord length (h). As discussed above the second group of vanes may extend from the hub radially outwards towards the outer ring. Alternatively, or additionally, one or more of said second groups of vanes may extend radially inwards from the circumferential outer ring into the space defined between adjacent vanes in said first group. Thus, gas turning can be effected from the inner zone of the TRS, the outer zone of the TRS or both.

The splitter vanes may advantageously be hollow in construction to minimise weight. This is particularly possible where the vanes are not load bearing vanes. Viewed from another aspect there is provided a turbine rear structure comprising a plurality of primary exhaust gas guide vanes extending radially from a central hub to a peripheral coaxial ring, the structure further comprising a plurality of intermediate exhaust gas guide vanes, wherein the intermediate exhaust gas guide vanes are arranged in the spaces defined between adjacent primary exhaust gas guide vanes, and wherein the intermediate vanes are located closer to one of the primary vanes than an opposing primary guide vane.

In effect the intermediate or splitter vanes are offset from a mid-point between adjacent primary vanes. Thus, the space between adjacent primary exhaust gas guide vanes comprises a pair of exhaust gas channels divided by the intermediate guide vane. One of the pair of channels may therefore have a larger cross-section than the second of the pair of channels.

Viewed from another aspect there is provided a gas turbine engine comprising a structure as described herein and an aircraft comprising one or more gas turbine engines described herein.

Viewed from yet another aspect there is provided a method of manufacturing a turbine rear structure, comprising the steps of

(A) forming a central hub and a circumferential outer ring,

(B) connecting a plurality of a first group of guide vanes so at to extend between the hub and the circumferential ring;

(C) positioning a second group of guide vanes between adjacent vanes of said first group,

wherein the second group of guide vanes are located asymmetrically with respect to adjacent vanes of said first group. The vanes may be formed using any suitable process. Advantageously the second group of guide vanes may be formed by an additive manufacturing process thereby allowing complex geometries to be achieved both internally and/or externally. This allows for still further optimisation. A more conventional way is to make the vanes out of sheet metal formed into the desired shape. Still further the turbine rear structure may be formed in its entirety by an additive manufacturing process.

Brief Description of the Drawings

One or more embodiments of the invention will now be described, by way of example only, and with reference to the following figures in which:

Figure 1A shows a par cross-section through an engine identifying the Turbine Rear Section (TRS); Figure 1 B shows a pair of adjacent guide vanes and solidity relationship; Figure 2 shows a front to aft view of a turbine rear structure (TRS); Figure 3 shows how separation of air flow can occur in a guide vane;

Figure 4 shows an intermediate splitter vane according to an invention described herein;

Figure 5 shows a perspective view of the intermediate guide vanes between two adjacent guide vanes;

Figure 6 shows the positioning of the intermediate guide vane with respect to two adjacent guide vanes;

Figure 7 shows the radial arrangement of intermediate guide vanes;

Figure 8 shows the chord-wise length of the intermediate vane with respect to two adjacent guide vanes;

Figures 9A and 9B show the pressure distribution along the length of the vane with and without the splitter vane described herein;

Figures 10A and 10B show figures 9A and 9B with the respective conventional vane and splitter vane arrangements; Figure 1 1 A, 1 1 B and 1 1 C illustrate the axial position of the splitter vane with respect to the suction peak; and Figures 12A and 12B show two arrangements of chord-wise position of the intermediate vane with respect to the adjacent vanes.

Any reference to prior art documents in this specification is not to be considered an admission that such prior art is widely known or forms part of the common general knowledge in the field. As used in this specification, the words "comprises", "comprising", and similar words, are not to be interpreted in an exclusive or exhaustive sense. In other words, they are intended to mean "including, but not limited to". The invention is further described with reference to the following examples. It will be appreciated that the invention as claimed is not intended to be limited in any way by these examples. It will also be recognised that the invention covers not only individual embodiments but also combination of the embodiments described herein.

The various embodiments described herein are presented only to assist in understanding and teaching the claimed features. These embodiments are provided as a representative sample of embodiments only, and are not exhaustive and/or exclusive. It is to be understood that advantages, embodiments, examples, functions, features, structures, and/or other aspects described herein are not to be considered limitations on the scope of the invention as defined by the claims or limitations on equivalents to the claims, and that other embodiments may be utilised and modifications may be made without departing from the spirit and scope of the claimed invention. Various embodiments of the invention may suitably comprise, consist of, or consist essentially of, appropriate combinations of the disclosed elements, components, features, parts, steps, means, etc, other than those specifically described herein. In addition, this disclosure may include other inventions not presently claimed, but which may be claimed in future.

Detailed Description

Figure 1 A shows the position of the turbine rear section (TRS) in a gas turbine engine. Figure 1 B shows a cross-section through a pair of adjacent guide vanes for a turbine rear structure (TRS). The TRS is located at the rear of the engine and provides a number of functions. For example, the TRS provides the structural connection for the engine to the aircraft body through lugs or mounts which are described below. Aerodynamically the TRS functions to cause exhaust gas that has been generated by the turbine in the engine to leave the engine in a generally axial direction - that is parallel with the axis of rotation of the shaft running along the centre-line of the engine.

Returning to figure 1 B, two adjacent vanes 1 , 2 are shown. Each vane comprises a leading edge 3 and a trailing edge 4 and an aerodynamic profile 5, consisting of a suction side S (primarily convex) and a pressure side P (primarily concave) extending there between on each side of the vane.

A TRS comprises a plurality of vanes and it will be recognised that the upper surface of vane 1 (shown in figure 1 ) forms the upper surface of the next pair of vanes (corresponding to vane 2) around the circumference of the TRS (described further below). A vane passage is defined between adjacent vanes around the TRS.

The leading edges of vanes 1 , 2 define an inlet passage 6 which in use receives exhaust gas from the turbine. Similarly the trailing edges of the vanes 1 , 2 define a outlet or exit 7 where exhaust gas leaves the TRS.

Between the leading and trailing edges the aerodynamic profile 5 acts to re-direct or turn the exhaust gas (as indicated by the arrow) so that the exhaust gas aligns more closely with the axis of the engine. This maximises the thrust generated by the exhaust gas by removing as much of the circulating component of the gas' movement as possible.

The circulating component of the exhaust gas is a result of the rotating and stationary turbine blades and vanes. This circulating or swirling component of movement can advantageously be harnessed to increase thrust.

Conventionally the aerodynamic profile 5 is selected so that the leading edge receives the circulating gas and vane passage (between adjacent vanes) guides or turns the gas by the appropriate amount. The precise shape of the profile 5 is therefore dependent on particular performance of the engine.

As engines become more powerful and more compact the component of swirl increases and thus a greater turning or re-directing effect is needed for the TRS to harness the exhaust gas energy for increased thrust. This has its own problems as described further below.

Figure 2 is a 'fore looking aft' view of a TRS i.e. looking in an exhaust gas flow direction. The TRS comprises a hub 8 and an outer circumferential ring 9 which is coaxial with the hub. The outer ring comprises a plurality of lugs 10 which may be connected to the aircraft body (for example a wing pylon).

Conventionally the TRS comprises a plurality of evenly spaced vanes extending from the hub to the ring and which each have a profile as shown in figure 1 . The profile is, as described above, optimised for the specific engine.

Figure 2 also illustrates the structural vanes (indicated by the hatched fill). The structural vanes provide the structural and load bearing connection between the hub and ring. The structural vanes comprise the same cross-section as shown in figure 1 but comprise internal structures providing the load path between the hub and the engine mounting lugs. All of the vanes may be load bearing or alternatively only some may be load bearing. Thus, non-load bearing vanes (indicated by the dotted fill) may be located adjacent to load bearing vanes.

As discussed above the profile of the vanes is optimised for the particular engine. An important parameter in TRS and vane design is the 'solidity' of the TRS vanes, in effect this is a measure of how much material occupies the space between the hub and the ring (noting that the TRS also has a length measured along the axis of the engine).

Solidity is calculated (referring to figure 1 ) as the ratio of :

Solidity = c / s

where:

s is the pitch between adjacent vanes; and

c is the chord-wise length of the vane.

Typical State of the Art (SoA) solidity c/s is in the range of -0.8 (0.4 < c/s < 1 .2). Figure 3 illustrates the limitation of conventional vane design. As described above, increases in engine power for modern engines increases the rotational component of gaseous flow within the engine. As the curvature of the aerodynamic portion increases (to accommodate the increased need to turn the circulating air in modern engines) the normal flow of air 1 1 shown by the dotted line in figure 3 begins to change.

Specifically, in normal operation the airflow 1 1 flows along the inner surfaces of the space between the adjacent vanes in a smooth manner. However, as the exhaust gas speed increases and the angle of turn become more aggressive (i.e. a greater turn angle) then separation may occur as shown by line 12. The exhaust gas then departs from contact with the inner surface of portion. Thus an inefficient exhaust gas flow is created.

Turning to figure 4, a TRS according to an invention described herein is shown. The TRS comprises the same general vane arrangement 1 , 2 as shown in figure 1. However, the structure further comprises an intermediate or interstitial splitter vane 13 located in the space between adjacent vanes. In effect the main vanes 1 , 2 define a first group of vanes and the intermediate vanes 13 define a second group of vanes, where each intermediate vane is located between two adjacent vanes in the first group.

As shown in figure 4, the intermediate vane is asymmetrically positioned with respect to the two adjacent vanes of group 1 . As shown by dotted line 14 the vane is located 'off-centre' and closer to one vane than the other. This asymmetrical spacing is repeated in the space between adjacent vanes.

In effect the intermediate vane splits the channel between adjacent vanes into two different flow paths identified by A and B in figure 4. It will thus be recognised that channel A is larger than channel B. It has been established by the inventor that introducing a channel difference in this way advantageously prevents separation of exhaust gas flowing along surface 15. Thus, reducing separation of exhaust gas allows for a greater turn angle to be achieved for a given engine.

This provides a number of synergistic advantages including:

The exhaust gas departure angle can be optimised without separation

A greater turn angle can be achieved in a shorter chord distance of the vane meaning the TRS can be shorter and lighter than a conventional TRS; A higher turbine power extraction/output can be used whilst optimising exhaust gas thrust from the rear of the TRS.

Figure 5 shows a portion of the circumference of the hub of a TRS according to an invention described herein. As shown the intermediate vane 13 is located closer to vane 2 than vane 1 creating the dissimilar flow channels on either side of the intermediate vane.

The inventor has established that the weight increase caused by the additional intermediate vanes can be compensated for by making only a subset of the vanes load bearing vanes the weight can thereby be reduced i.e. the number of main vanes (the first group of vanes) may be reduced.

Depending on the exact requirements an invention described herein allows for either a reduction in the number of load bearing vanes (these vanes including the internal load bearing struts or members) or an increase in the number of intermediate vanes or retaining the same number of load bearing vanes and including the intermediate vanes. With the same number of vanes plus splitter vanes in between, a larger turning angle can be obtained. Figure 6 shows an end view of the TRS illustrating the positioning of the intermediate vane 13 with respect to the two opposing vanes 1 , 2.

As shown the intermediate vane is not positioned centrally with respect to the two adjacent vanes but instead is closer to vane 2 than vane 1. Vane 2 represents the vane that is upstream of vane 1 in respect of the flow of circulating exhaust gas i.e. exhaust gas impinges against vane 2 first. Thus, each intermediate vane is located closer to the 'upstream' vanes of the TRS as opposed to the downstream side.

The intermediate vane may be located at any position that is asymmetrical with respect to the vanes 1 , 2. However, the inventor has established that the intermediate vane may be advantageously positioned approximately 1/3 ^rd of the distance between the two adjacent vane.

Referring to figures 6 and 8, the inventor has established that, advantageously, the following conditions may be met to optimise the performance of the TRS: a < b a = 1/3 of d +/- 1/6 of d

where d is equal to the pitch s shown in figure 1 B.

Figure 6 also illustrates another advantageous feature that the inventor has established. Specifically the radial extent of the vane 13 from the hub may be selected so that the intermediate vane terminates part way across the radius between the hub and the outer ring.

As shown in figure 6, the intermediate vane may extend a predetermined distance from the hub depending on the specific parameters of the given engine. For example, the intermediate vane may extend to r-ι, r ₂ or r ₃ i.e. increase radii from the hub. Each intermediate vane may extend by the same distance or alternating or groups of intermediate vanes may extend by different distances.

In an alternative arrangement all or a subset of vanes may extend the full radius between hub and outer ring.

This is illustrated in figure 7 where the load bearing vanes 1 , 2 can be seen with intermediate vanes 13 located asymmetrically there between and terminating at a radius less than the full radius of the outer ring (measured from the hub).

Advantageously terminating the intermediate vanes at a distance less than the full radius of the outer ring provides a number of advantages including (but not limited to): there is no thermal loading of the intermediate vane. Providing the intermediate vane with a free end allows the vane to expand as it heats (from the hot exhaust gas) without being compressed against the outer ring

each intermediate vane can be selected so as to be optimised to direct circulating exhaust gas at the location of greatest circulation. The swirl or circulating component of the flow is in general strongest at the inner ring and decreases toward the outer ring. Thus, the intermediate vanes are most effective at the centre; and

the weight of each intermediate vane can be minimised since the vane only extends to a distance where it provides an advantageous effect.

Figure 7 also illustrates a further feature of radially inwardly extending intermediate vanes 14. Such radially inwardly extending vanes may be used where circulating exhaust gas requires re-direction at the inner surface of the outer ring. This may be advantageously positioned at the same 1/3 ^rd spacing described above. As shown in figure 7 the inwardly extending vane may align with the outwardly extending intermediate vane. It may also be used in isolation.

Figure 8 shows the chord-wise extend and position of the intermediate vanes with respect to the adjacent vanes 1 , 2.

The inventor has established that the intermediate vanes may advantageously extend in a chord-wise direction by a particular distance. Specifically the inventor has established that the following condition must be satisfied to optimise the TRS: e ranges between 20% of c and 100% of c

Advantageously: e = ½ of c

Figures 9A and 9B show the pressure distribution along the length of the vane with and without the splitter vane described herein. Each graph shows pressure on the y axis and axial position on the x axis and illustrates the negative pressure which is created on the convex face of the vane i.e. the upper side of the vane as shown for example in figure 1 .

The difference in pressure profiles and the lowest pressures (suction peak) can be seen in each figure. Specifically the magnitude of negative pressure is clearly shown to be significantly different between a conventional arrangement of 9A and the arrangement comprising a conventional vane and splitter vane. As shown in 9B the magnitude of negative pressure for both the conventional vane and the splitter vane are both reduced.

It will be recognised that a reduction in the peak negative pressure (the suction peak) reduces the chance of air (exhaust) gas flow separation from the surface of the vane. By maintaining contact with the vane the turning ability of the vanes is increased. Advantageously, as shown in figure 9B, the negative peak pressure on both the load bearing conventional vanes and the splitter vanes are reduced and thus the chance of separation is also reduced. The turning ability of both vanes is therefore increased. Figure 10A shows the same regular vane pressure distribution as shown in figure 9A. However, in figure 10A the graph is aligned with the vane illustrating the locations of the respective (negative) pressures along the axial direction x/c. Figure 10B shows the effect of the splitter vane, again in alignment with the vane and splitter vanes according to the invention. The dashed line in figure 10B illustrates the position of the pressure peak on the splitter vane.

Figures 1 1 A, 1 1 B and 1 1 C illustrate the axial position of the splitter vane with respect to the suction peak described above.

Referring to figure 1 1A the suction peak point is illustrated by the circle positioned on the convex side of the splitter vane.

The inventor has established the following relationship between the position of the splitter vane with respect to the suction peak: Splitter vane (axial) chord: h = i + j

0% of h < i < 100% of h

Thus, the splitter vane must be located such that at least a part of the vane is located over the suction peak. More specifically, it has been established that the optimum position of the suction peak lies within the range of i = 25% ±15% of h.

Figures 1 1 B and 1 1 C illustrate the two extreme positions of the splitter vane. The splitter vane needs to overlap the suction peak region, i. e. the splitter vane leading edge (LE) cannot be further downstream than the main vane suction peak and the splitter vane trailing edge (TE) cannot be further upstream than the main vane suction peak.

Figures 12A and 12B show two arrangements of chord-wise position of the intermediate vane with respect to the adjacent vanes. Figures 12A and 12B illustrate two alternative positions of the intermediate vane. In figure 12A the intermediate vane is recessed by distance f within the space defined between the adjacent vanes 1 , 2. In figure 9A there is increased incidence robustness compared to a configuration without the splitter vanes. Conversely Figure 12B illustrates an arrangement when the intermediate vane leads or extends beyond the leading edge of the vane 2 by distance g. In figure 9B there is the potential to reduce the upstream forcing on the rotor (static pressure disturbances impacting the upstream turbine rotor in a negative way).

The arrangements described herein may be manufactured using any suitable technique such as casting, conventional machining or hydroforming. These techniques allow the aerodynamic shapes to be formed to define the desired geometry which is itself defined by the particular engine.

Additive manufacturing technique may also be conveniently used to form either components of the TRS (such as the intermediate vanes) or to form the entire TRS. Additive manufacturing technique involve building up a 3 dimensional shape as a series or layers, for example using a powder bed technique such as laser beam melting or the like. Intricate geometries may be conveniently formed with minimal material wastage. The described embodiment may be particularly beneficial when the aero-surfaces are formed of sheet material, which is known in the field as a fairing design.

Example materials for the vanes and splitter vanes include Inconel 718, Haynes 282 or other similar super-alloys or combinations thereof.

Example sizes of the splitter vanes may be as follows:

In a first example (Engine 1 ) each splitter vane may be 800 mm in radius, vane chord c = 250 mm with 14 vanes in the TRS.

In a second example (Engine 2) each splitter vane may be 450 mm in radius, vane chord c = 170 mm, with 10 vanes in the TRS.

Examples of additive manufacturing techniques that may be used to form all or part of an invention described herein include but are not limited to:

Powder bed fusion methods

Direct metal laser sintering (DMLS)

Electron beam melting (EBM)

Selective laser melting (SLM)

Selective laser sintering (SLS)

Direct metal wire deposition Direct metal powder deposition