JP2013064535A - Gas turbine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress variation of pressure at a downstream part of a tail pipe.SOLUTION: In this gas turbine, at the downstream part of the tail pipe 20 of a combustor, the inner surfaces 24 of a pair of lateral walls 22 facing each other in the circumferential direction C of a turbine rotor form inclination surfaces 25 that, going downstream in a direction of an axial line Ac of the tail pipe 20, incline in a direction approaching the tail pipe of an adjacent other combustor that gradually draws closer, until the inclination surfaces reach the downstream end 20e of the tail pipe 20.

Description

  The present invention relates to a gas turbine comprising: a plurality of combustors that mix and burn fuel with compressed air to generate combustion gas; and a turbine having a rotor that is rotated by the combustion gas from the plurality of combustors. In particular, it relates to a combustor tail tube.

  The gas turbine includes a compressor that takes in outside air to generate compressed air, a plurality of combustors that generate combustion gas by mixing fuel with the compressed air, and a rotor that is rotated by the combustion gas from the plurality of combustors. Having a turbine. The plurality of combustors are annularly arranged around the rotor. Each combustor has a tail tube that delivers combustion gas to the gas inlet of the turbine.

  When the combustion gas flows out of the transition piece of the combustor, it enters the combustion gas flow path of the turbine from the gas inlet of the turbine. At this time, immediately after the combustion gas flows out of the transition piece, a Karman vortex street is formed in the flow, and unsteady pressure fluctuations using this Karman vortex street as a vibration source resonate with the acoustic eigenvalue, resulting in large pressure fluctuations. May occur, resulting in an operating load.

  Therefore, in the technique described in Patent Document 1 below, the dimension in the axial direction between the downstream end of the transition piece and the upstream end of the first stage stationary blade, the upstream end of the first stage stationary blade and the rotor are the center. A large pressure fluctuation is suppressed by limiting the dimension in the circumferential direction between the center portions adjacent to each other in the circumferential direction to a specific range.

JP 2009-197650 A

  The technique described in Patent Document 1 can certainly suppress a large pressure fluctuation in the downstream portion of the transition piece. However, it is desired to further suppress the pressure fluctuation in the downstream portion of the transition piece and further increase the gas turbine efficiency.

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a gas turbine that can further suppress gas pressure fluctuation in the downstream portion of the combustor tail pipe and further improve gas turbine efficiency in order to meet such a demand.

A gas turbine according to the invention for achieving the above object is as follows:
A plurality of combustors for generating combustion gas by mixing fuel with compressed air and a turbine having a rotor rotated by the combustion gas from the plurality of combustors, the plurality of combustors comprising the rotor And a pair of side walls facing each other in the circumferential direction of the rotor at a downstream portion of the tail cylinder of the combustor. The inner surface of at least one of the side walls gradually reaches the downstream end of the transition piece toward the downstream side in the axial direction of the transition piece so as to approach the transition piece of another adjacent combustor. It forms the inclined surface which inclines, It is characterized by the above-mentioned.

  Since the combustion gas flowing toward the downstream side in the transition piece tries to flow in the direction along the inner surface of the side wall of the transition piece after flowing out of the transition piece, the Karman vortex street is located downstream of the downstream end face of the transition piece. May be formed.

  In the gas turbine, since the inner surface of the side wall on the downstream side of the transition piece forms an inclined surface until it reaches the downstream end of the transition piece, the flows along the inner surface of the side wall of the transition piece adjacent to each other Since it joins at an angle to the downstream side of the downstream end face of the cylinder, it is possible to suppress the formation of a Karman vortex street on the downstream side of the downstream end face of the tail cylinder, and to suppress the pressure fluctuation in the downstream part of the tail cylinder.

  Here, in the gas turbine, the turbine has a plurality of first stage stationary blades arranged annularly around the rotor and along the gas inlet, and the first stage stationary blades are chords The chord direction in which the blade extends is inclined with respect to the circumferential direction, and the side where the downstream end of the first stage stationary blade exists is inclined with respect to the upstream end of the first stage stationary blade in the circumferential direction. In this case, the at least one side wall of the transition piece is preferably the side wall on the blade inclination side of the pair of sidewalls facing each other in the circumferential direction of the transition piece.

  Of the pair of side walls facing each other in the circumferential direction of the transition piece, when the inner surface of only the blade inclined side wall is an inclined surface, the direction of the combustion gas guided by this inclined surface and the first stage stationary blade The direction of the flow of the introduced combustion gas becomes substantially the same, and the flow of the combustion gas from the transition piece to the first stage stationary blade becomes smooth. For this reason, even if the inner surface of only the side wall on the blade inclination side is an inclined surface, the pressure fluctuation in the downstream portion of the tail tube can be effectively suppressed. The chord is a line segment connecting the upstream end and the downstream end of the stationary blade.

  In the gas turbine, it is preferable that the inner surfaces of both of the pair of side walls facing each other in the circumferential direction of the tail tube form the inclined surface.

  In the gas turbine, it is possible to suppress the formation of a Karman vortex street on the downstream side of each downstream end surface of the transition piece that is continuous from the inner surfaces of the pair of side walls of the transition piece.

  Further, in the gas turbine, on the basis of the circumferential dimension B from the upstream end to the downstream end of the inclined surface, the ratio A / B of the axial dimension A from the upstream end to the downstream end is: It is preferable that it is 1 or more and 8 or less.

  In the gas turbine, the inclined surface may include at least part of a curved surface that approaches the axis of the tail cylinder and smoothly swells toward the downstream side.

  In the gas turbine, a ratio of the number of the combustors to the number of the first stage stationary blades is an odd number of 2: 3 or more, and the pitch dimension P of the plurality of first stage stationary blades is used as a reference. The ratio S / P of the circumferential dimension S from the intermediate point between the transition piece of the combustor and the transition piece of the other combustion unit to the upstream end of the first stage stationary blade closest in the circumferential direction is , 0.05 or less, between 0.2 and 0.55, and between 0.7 and 1.0.

  In the gas turbine, one of the first stage stationary blades exists relatively close in the circumferential direction to each downstream end of the transition piece connected from each of the inner surfaces of the pair of side walls of the transition piece of any combustor. Therefore, the presence of this first stage stationary blade can suppress the pressure fluctuation on the downstream side of each transition piece.

  Further, in the gas turbine, the ratio of the dimension L in the axial direction from the downstream end of the transition piece to the upstream end of the first stage stationary blade, based on the pitch dimension P of the plurality of first stage stationary blades L / P is preferably 0.2 or less.

  In the gas turbine, since the first stage stationary blades are relatively close to the downstream end of the tail cylinder in the axial direction of the tail cylinder, the presence of the first stage stationary blades causes each tail Pressure fluctuation on the downstream side of the cylinder can be suppressed.

  In the present invention, it is possible to suppress the formation of a Karman vortex street on the downstream side of the downstream end face of the transition piece, and it is possible to suppress the pressure fluctuation in the downstream portion of the transition piece. For this reason, according to the present invention, the gas turbine efficiency can be increased.

It is the whole side view which notched the principal part of the gas turbine in one Embodiment which concerns on this invention. It is sectional drawing around the combustor of the gas turbine in one Embodiment which concerns on this invention. It is a perspective view of a transition piece in one embodiment concerning the present invention. It is sectional drawing of the downstream of the transition piece in one Embodiment which concerns on this invention. It is a graph which shows the relationship between the inclination rate of the inclined surface in one Embodiment which concerns on this invention, and a pressure fluctuation range. It is explanatory drawing which shows the positional relationship of the transition piece and 1st stage stationary blade in one Embodiment which concerns on this invention. It is explanatory drawing which shows the pressure fluctuation of the downstream of the transition piece in one Embodiment which concerns on this invention, The figure (a) shows the case where the circumferential direction ratio is 10%, The figure (b) shows the circumferential direction ratio. FIG. 5C shows a case where the circumferential ratio is 35%, and FIG. 4D shows a case where the circumferential ratio is 47.5%. It is a graph which shows the relationship between the pressure fluctuation width of the downstream of the transition piece of one Embodiment which concerns on this invention, and the circumferential direction ratio. It is sectional drawing of the downstream of the transition piece for showing the modification of the inclined surface of one Embodiment which concerns on this invention, The figure (a) shows the 1st modification of an inclined surface, The figure (b) The 2nd modification of an inclined surface is shown. It is explanatory drawing which shows the positional relationship of the inclined surface of a transition piece, and a 1st step | paragraph stationary blade in the modification of one Embodiment which concerns on this invention.

  Hereinafter, an embodiment of a gas turbine according to the present invention will be described in detail with reference to the drawings.

  As shown in FIG. 1, the gas turbine according to the present embodiment generates a combustion gas by combusting a compressor 1 that compresses outside air to generate compressed air and fuel from a fuel supply source mixed with the compressed air. A plurality of combustors 10 and a turbine 2 driven by combustion gas are provided.

  The turbine 2 includes a casing 3 and a turbine rotor 5 that rotates in the casing 3. The turbine rotor 5 includes a rotor main body 6 configured by laminating a plurality of rotor disks, and a plurality of moving blades 7 extending in a radial direction from the rotor disks for each of the plurality of rotor disks. That is, the turbine rotor 5 has a multistage rotor blade configuration. The turbine rotor 5 is connected to, for example, a generator (not shown) that generates electricity by the rotation of the turbine rotor 5. A plurality of stationary blades 4 extending from the inner peripheral surface of the casing 3 in the direction approaching the rotor body 6 are fixed to the upstream side of the moving blades 7 of each stage.

  The plurality of combustors 10 are fixed to the casing 3 at equal intervals in the circumferential direction around the rotation axis Ar of the turbine rotor 5.

  As shown in FIG. 2, the combustor 10 includes a tail cylinder 20 that sends high-temperature and high-pressure combustion gas G from a gas inlet 9 of the turbine 2 into the gas flow path 8 of the turbine 2, and fuel and fuel in the tail cylinder 20. And a fuel supplier 11 for supplying the compressed air Air. The moving blade 7 and the stationary blade 4 of the turbine 2 are arranged in the gas flow path 8. The fuel supplier 11 supplies pilot fuel X into the tail cylinder 20, premixes the pilot burner 12 that forms a diffusion flame in the tail cylinder 20, the main fuel Y, and the compressed air Air, and performs premixing. A plurality of main nozzles 13 that supply gas as a gas into the transition piece 20 and form a premixed flame in the transition piece 20 are provided.

  As shown in FIGS. 2 and 3, the transition piece 20 has a cylindrical shape, and is provided at a body 21 through which combustion gas G flows on the inner peripheral side, and at a downstream end portion of the body 21. And an outlet flange 31 that spreads away from the head.

  The cross-sectional shape of the downstream side of the body 21 is rectangular, and the body 21 has a pair of side walls 22 facing each other in the circumferential direction C around the rotation axis Ar of the turbine rotor 5, and the downstream side. A pair of side walls 23 facing each other in the radial direction about the rotation axis Ar.

  As shown in FIG. 4, the outlet flange 31 provided at the downstream end of the body 21 includes a flange main body 32 that extends from the downstream end of the body 21 in a direction away from the axis Ac of the tail cylinder 20, and this flange. And an opposing portion 33 extending from the outer edge of the main body portion 32 toward the upstream side. The downstream end surface of the flange main body portion 32 forms the downstream end surface 20ea of the transition piece 20. Further, a seal member 35 is provided between the facing portion 33 and the facing portion 33 of the transition piece 20 of the combustor 10 adjacent in the circumferential direction C to seal between the transition pieces of the adjacent combustors 10. ing. In the present embodiment, the downstream portion of the body 21, that is, the side walls 22 and 23 on the downstream side of the body 21, and the flange main body 32 are formed as an integrally molded product.

  The inner surfaces 24 of the pair of side walls 22 facing each other in the circumferential direction C gradually approach the tail cylinder 20 of another combustor 10 adjacent to the downstream side in the axis Ac direction of the tail cylinder 20. An inclined surface 25 that is inclined to reach the downstream end 20e of the transition piece 20 is formed. That is, the downstream end of the inclined surface 25 is the downstream end 20 e of the tail cylinder 20.

  The combustion gas G flowing toward the downstream side in the transition piece 20 tends to flow in the direction along the inner surface 24 of the side wall 22 even after flowing out of the transition piece 20, so that the downstream end face 20 ea of the flange main body portion 32 A Karman vortex street may be formed downstream.

  In the present embodiment, since the inner surface 24 of the side wall 22 on the downstream side of the tail cylinder 20 forms an inclined surface 25, the angle formed by the downstream end surface 20 ea of the flange main body portion 32 with respect to the inner surface 24 of the side wall 22 becomes small. . Therefore, in the present embodiment, Karman vortex streets can be prevented from being formed on the downstream side of the downstream end face 20ea of the flange main body 32, and pressure fluctuations in the downstream portion of the tail cylinder 20 can be suppressed.

  Here, since the pressure fluctuation width of the downstream side portion of the transition piece 20 when the inclination rate of the inclined surface 25 is changed is simulated, the simulation result will be described. In this simulation, as shown in FIG. 4, from the upstream end 25 s on the basis of the dimension B in the circumferential direction C from the upstream end 25 s of the inclined surface 25 to the downstream end 20 e (= the downstream end of the transition piece 20). The ratio A / B of the dimension A in the axis Ac direction to the downstream end 20 e is defined as the inclination rate of the inclined surface 25.

  As a result of this simulation, as shown in FIG. 5, it was found that when the gradient A / B is 1 or more and 8 or less, the pressure fluctuation width ΔP in the downstream portion of the combustor 10 becomes small. This is because when the slope ratio A / B is less than 1 and greater than 8, the slope is too steep or too slow, so that the effect as the slope 25 cannot be sufficiently obtained. Furthermore, it was also found that the pressure fluctuation width ΔP becomes extremely small when the inclination ratio A / B of the inclined surface 25 is 2 or more and 6 or less. Note that, as the flow velocity of the combustion gas G flowing in the transition piece 20 increases, the pressure fluctuation range ΔP also increases, but the relationship between the inclination rate A / B of the inclined surface 25 and the pressure fluctuation range ΔP is as follows. This is basically the same even if the flow velocity of the combustion gas G flowing through 20 changes.

  For this reason, it can be said that the preferable range Ra of the inclination rate A / B of the inclined surface 25 is 1 or more and 8 or less, and the more preferable range Rb is 2 or more and 6 or less.

  Furthermore, since the pressure fluctuation width in the downstream portion of the combustor 10 when the relative position between the transition piece 20 and the first stage stationary blade 4a is changed is simulated here, the simulation result is also described. To do. Specifically, as shown in FIG. 6, with reference to the pitch dimension P in the circumferential direction C of the plurality of first stage stationary blades 4a, the transition piece 20 of the specific combustor 10a and one of the circumferential direction C The ratio S of the dimension S in the circumferential direction C from the intermediate point M with the transition piece 20 of the other combustor 10b adjacent to the side to the upstream end 4s of the first stage stationary blade 4a closest to one side in the circumferential direction C The relationship between / P (hereinafter referred to as circumferential ratio S / P) and pressure fluctuation range ΔP was simulated.

  In this simulation, the ratio between the number Nc of the combustors 10 and the number Ns of the first stage stationary blades 4a is 2: 3, and the inclination rate A / B of the inclined surface 25 of the tail cylinder 20 is 2.75. went. Further, this simulation is based on the pitch dimension P, and the ratio L / P of the dimension L in the axis Ac direction from the downstream end 20e of the transition piece 20 to the upstream end 4s of the first stage stationary blade 4a (hereinafter referred to as the axis line). The direction ratio L / P) was 12%.

  As shown in FIG. 8, when the axial ratio L / P was 12%, there was almost no unsteady pressure fluctuation when the circumferential ratio S / P was 0% to 5%. However, when the circumferential direction ratio S / P exceeded 5%, a large pressure fluctuation range ΔP began to be seen, and when the circumferential direction ratio S / P reached 10%, the pressure fluctuation range ΔP became larger.

  As shown in FIG. 7 (a), when the circumferential ratio S / P is 10%, the transition piece 20 of a specific combustor 10a and the other combustor 10b adjacent to one side in the circumferential direction C of the specific combustor 10a. Although no unsteady pressure fluctuation is observed on the downstream side with respect to the transition piece 20, the tail section 20 of the specific combustor 10 a and the tails of the other combustors 10 c adjacent to the other side in the circumferential direction C. A Karman vortex street v was generated on the downstream side between the cylinder 20 and a relatively large unsteady pressure fluctuation occurred. This is because the first stage stationary blade closest in the circumferential direction C from between the transition piece 20 of the specific combustor 10a and the transition piece 20 of the other combustor 10c adjacent to the other side in the circumferential direction C. This is probably because the dimension in the circumferential direction C up to the upstream end 4s of 4a is increased. In addition, the thin line in FIG. 8 has shown the isostatic pressure line.

  Therefore, it is considered that when the circumferential ratio S / P is 10%, the pressure fluctuation range ΔP is increased. However, in this simulation, the inclination rate A / B of the inclined surface 25 is 2.75 which is in a more preferable range Rb (2 or more and 6 or less), and therefore, when the inclined surface 25 is not formed. Is smaller than the pressure fluctuation range ΔP.

  As shown in FIG. 8, the pressure fluctuation width ΔP decreases rapidly as the circumferential ratio S / P becomes 20%, and when the circumferential ratio S / P becomes 22.5%, the unsteady pressure fluctuation is almost not. I can no longer see it. As shown in FIG. 7B, when the circumferential ratio S / P is 22.5%, the transition piece 20 of the specific combustor 10a and another combustor adjacent to this on one side in the circumferential direction C. The downstream side between the transition piece 20 of the 10b and the downstream side between the transition piece 20 of the specific combustor 10a and the transition piece 20 of the other combustor 10c adjacent to the other side in the circumferential direction C. However, almost no steady pressure fluctuation was observed.

  As shown in FIGS. 7C and 7D, unsteady pressure fluctuation was hardly observed even when the circumferential ratio S / P was 35% or 47.5%. However, as shown in FIG. 8, when the circumferential ratio S / P exceeds 55%, a large pressure fluctuation range ΔP starts again, and when the circumferential ratio S / P reaches 60%, the pressure fluctuation range ΔP. Became larger. This is because the first stage stationary blade closest in the circumferential direction C from between the transition piece 20 of the specific combustor 10a and the transition piece 20 of the other combustor 10b adjacent to the one side in the circumferential direction C. This is probably because the dimension in the circumferential direction C up to the upstream end 4s of 4a is increased. That is, when the circumferential ratio S / P is 60%, it is considered that the same phenomenon occurs for basically the same reason as when the circumferential ratio S / P is 10%.

  This pressure fluctuation range ΔP decreased rapidly when the circumferential ratio S / P was 70%, and almost no unsteady pressure fluctuation was observed when the circumferential ratio S / P was 72.5%. Thereafter, almost no unsteady pressure fluctuation is observed until the circumferential ratio S / P reaches 100%.

  As described above, when the circumferential ratio S / P is 0% to 5%, 20% to 55%, and 70% to 100%, there is almost no unsteady pressure fluctuation, and the pressure in the downstream portion of the tail tube 20 It was found that the fluctuation range ΔP is very small. That is, it was found that preferable ranges Rc in the circumferential direction ratio S / P are 0% to 5%, 20% to 55%, and 70% to 100%.

  Furthermore, here, the axial direction ratio L / P was changed, and the relationship between the circumferential direction ratio S / P and the pressure fluctuation range ΔP was simulated in the same manner as described above.

  As shown in FIG. 8, even when the axial direction ratio L / P is 18%, 20%, or 27%, the change in the pressure fluctuation width ΔP with respect to the change in the circumferential direction ratio S / P The same tendency as when the direction ratio L / P was 12% was observed. That is, when the axial direction ratio L / P is 12%, the circumferential direction ratio S / P is 0% to 5%, 20% to 55%, and 70% to 100%. It was found that the pressure fluctuation width ΔP in the downstream portion of the combustor 10 is relatively small as compared with the cases where P is 5% to 20% and 55% to 70%.

  However, when the axial direction ratio L / P is 18% and 20%, when the circumferential direction ratio S / P is 0% to 5%, 20% to 55%, 70% to 100%, the axial direction ratio L described above. As in the case where / P is 12%, there is almost no unsteady pressure fluctuation and the absolute value of the pressure fluctuation width ΔP is small, but when the axial direction ratio L / P is 27%, the circumferential ratio S / P It was found that the absolute value of the pressure fluctuation range ΔP is large even when 0 is 5%, 20% to 55%, and 70% to 100%.

  That is, it was found that the pressure fluctuation range ΔP is reduced by setting the axial direction ratio L / P to 20% or less.

  The above simulation results are obtained when the ratio of the number Nc of the combustors 10 and the number Ns of the first stage stationary blades 4a is 2: 3. Nc: Ns = 2: 5, Nc: Ns Even when = 2: 7, Nc: Ns = 2: 9 or more, the relationship between the relative position between the transition piece 20 and the first stage stationary blade 4a and the pressure fluctuation width ΔP in the downstream portion of the transition piece 20 is It is considered that the same result as above can be obtained. However, as the number Ns of the first stage stationary blades 4a increases with respect to the number Nc of the combustors 10, the pressure fluctuation width ΔP increases regardless of the circumferential ratio S / P and the axial ratio L / P. When the absolute value of the pressure fluctuation width ΔP at the time becomes smaller and the number Ns of the first stage stationary blades 4a becomes larger, the unsteady pressure can be obtained regardless of the circumferential direction ratio S / P and the axial direction ratio L / P. It is thought that almost no change will be seen.

  When the ratio between the number Nc of the combustors 10 and the number Ns of the first stage stationary blades 4a is 1: a natural number, the ratio between the transition piece 20 of each combustor 10 and the other transition piece 20 adjacent to it. Since the upstream end 4s of the first stage stationary blade 4a can be disposed immediately below, the unsteady pressure fluctuation can be almost eliminated by arranging the first stage stationary blade 4a in this way.

  Next, various modifications of the inclined surface 25 of the transition piece 20 will be described.

  The inclined surface 25 of the above embodiment is entirely flat from the upstream end 25s to the downstream end 20e. However, the inclined surface 25 does not need to be entirely flat, and may include a curved surface at least partially. Good.

  Specifically, as shown in FIG. 9, the curved surfaces are curved surfaces 26 a, 26 b, and 26 c that swell smoothly toward the downstream side toward the axis Ac of the tail cylinder 20. For example, the curved surface 26a is formed in the boundary region between the inclined surface 25 and the downstream end surface 20ea of the flange main body 32, that is, the downstream end of the curved surface 26a is the downstream end 20e of the inclined surface 25, as shown in FIG. Matches. Further, the curved surface 26 b has the upstream end of the curved surface 26 b coincident with the upstream end 25 s of the inclined surface 25. Further, as shown in FIG. 5B, the entire inclined surface 25 is a curved surface 26c.

  As described above, when a curved surface is employed as at least a part of the inclined surface 25, there is no place where the flow direction of the combustion gas G changes rapidly, and thus a Karman vortex street is formed on the downstream side of the downstream end surface 20ea of the tail cylinder 20. This can be suppressed more effectively, and the pressure fluctuation in the downstream portion of the transition piece 20 can be more effectively suppressed. For this reason, when a curved surface is adopted as at least a part of the inclined surface 25, the preferable range Ra of the inclination ratio A / B of the inclined surface 25 is 1 or more and 8 or less as described above.

  In the above embodiment, the inner surfaces 24 of the pair of side walls 22 facing each other in the circumferential direction C form the inclined surface 25, but only one of the inner surfaces 24 forms the inclined surface 25. In addition, the pressure fluctuation in the downstream portion of the transition piece 20 can be suppressed. In this case, as shown in FIG. 10, in the circumferential direction C, the side where the downstream end 4e of the first stage stationary blade 4a exists with respect to the upstream end 4s of the first stage stationary blade 4a is the blade inclined side Ca. Of the pair of side walls 22 (22a and 22b in the case of FIG. 10) facing each other in the circumferential direction C, the inner surface 24 of the side wall 22 (22b in the case of FIG. 10) on the blade inclination side Ca forms an inclined surface 25. It is preferable. This is because the direction of the flow of the combustion gas G guided by the inclined surface 25 and the chord direction which is a line segment connecting the upstream end 4s and the downstream end 4e of the first stage stationary blade 4a, that is, the first stage stationary blade. The flow direction of the combustion gas G guided by 4a is almost the same, the flow of the combustion gas G from the tail cylinder 20 to the first stage stationary blade 4a becomes smooth, and the pressure fluctuation in the downstream portion of the tail cylinder 20 is reduced. This is because it can be effectively suppressed.

  As described above, of the pair of side walls 22 facing each other in the circumferential direction C, only the inner surface 24 of one of the side walls 22 (22a and 22b in the case of FIG. 10) forms the inclined surface 25. However, the relationship between the relative position of the transition piece 20 and the first stage stationary blade 4a and the pressure fluctuation width ΔP in the downstream portion of the transition piece 20 is basically the same as the above simulation result.

  1: compressor, 2: turbine, 3: casing, 4: stationary blade, 4a: first stage stationary blade, 4s: upstream end (of stationary blade), 4e: downstream end (of stationary blade), 5: turbine rotor, 6 : Rotor body, 7: moving blade, 8: gas flow path, 9: gas inlet, 10: combustor, 20: tail tube, 20e: downstream end (of or inclined surface of tail tube), 20ea: (of tail tube) or downstream end surface (of flange main body), 21: body, 22, 22a, 22b, 23: side wall, 24: inner surface, 25: inclined surface, 25s: upstream end (of inclined surface), 26a, 26b, 26c: curved surface

Claims (7)

A plurality of combustors for mixing combustion with compressed air to generate combustion gas, and a turbine having a rotor rotated by the combustion gas from the plurality of combustors,
A plurality of combustors are annularly arranged around the rotor, and a gas turbine having a tail tube that sends combustion gas to a gas inlet of the turbine,
The inner surface of at least one of the pair of side walls facing each other in the circumferential direction of the rotor at the downstream portion of the transition piece of the combustor is directed toward the downstream side in the axial direction of the transition piece, The inclined surface which inclines to the downstream end of the transition piece in a direction approaching the transition piece of another adjacent combustor gradually,
A gas turbine characterized by that. The gas turbine according to claim 1, wherein
The turbine has a plurality of first stage stationary blades arranged annularly around the rotor and along the gas inlet, and the first stage stationary blade has a chord direction in which the chord extends in the circumferential direction. Inclined with respect to the direction,
In the circumferential direction, when the side where the downstream end of the first stage stationary blade exists with respect to the upstream end of the first stage stationary blade is a blade inclined side, the at least one side wall of the tail tube is Of the pair of side walls facing each other in the circumferential direction in the tail cylinder, the side wall on the blade inclination side,
A gas turbine characterized by that. The gas turbine according to claim 1, wherein
The inner surfaces of both of the pair of side walls facing each other in the circumferential direction in the tail tube form the inclined surface.
A gas turbine characterized by that. The gas turbine according to any one of claims 1 to 3,
On the basis of the circumferential dimension B from the upstream end to the downstream end of the inclined surface, the ratio A / B of the axial dimension A from the upstream end to the downstream end is 1 or more and 8 or less. ,
A gas turbine characterized by that. In the gas turbine according to any one of claims 1 to 4,
The inclined surface includes, at least in part, a curved surface that approaches the axis of the tail tube and smoothly bulges toward the downstream side.
A gas turbine characterized by that. The gas turbine according to any one of claims 1 to 5,
A ratio of the number of the combustors and the number of the first stage stationary blades is an odd number of 2: 3 or more;
Based on the pitch dimension P of the plurality of first stage stator blades, the first stage stator blades closest in the circumferential direction from an intermediate point between the tail cylinder of the combustor and the tail cylinder of the other combustor The ratio S / P of the circumferential dimension S to the upstream end is 0.05 or less, between 0.2 and 0.55, and between 0.7 and 1.0.
A gas turbine characterized by that. The gas turbine according to any one of claims 1 to 6,
The ratio L / P of the dimension L in the axial direction from the downstream end of the transition piece to the upstream end of the first stage stationary blade is 0.2 based on the pitch dimension P of the plurality of first stage stationary blades. Is
A gas turbine characterized by that.

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