JP2021169800A - High-temperature component and rotary machine - Google Patents

Abstract

To suppress a blockage risk due to a foreign matter in a cooling passage of a high-temperature component.SOLUTION: A high-temperature component 50, 51 includes: multiple first cooling passages 61 extending linearly; and multiple second cooling passages 62 separating from the first cooling passages in a perpendicular direction to a plane including extending directions of the multiple first cooling passages and extending along the extending directions of the first cooling passages so as to be respectively communicated to any of the first cooling passages. Each of the first cooling passages has a maximum value of the sectional area thereof that is larger than a maximum value of the sectional area of a second cooling passage that is located nearest to the first cooling passage within a cross section orthogonal to the extending directions.SELECTED DRAWING: Figure 5

Description

The present disclosure relates to high temperature parts and rotary machines.

For example, in a machine such as a gas turbine through which a high-temperature working gas flows, the parts constituting the machine include high-temperature parts that require cooling by a cooling medium. As a cooling structure for such a high-temperature component, it is known that the high-temperature component is cooled by circulating cooling air inside the component (see, for example, Patent Document 1).

JP-A-2015-92074

In a machine operated by a high-temperature working gas such as a gas turbine, in general, the removal of heat by cooling leads to a decrease in the thermal efficiency of the machine. Therefore, it is desirable to efficiently cool high-temperature parts with as few cooling media as possible. Therefore, it is desirable to increase the flow rate of the cooling medium in the cooling passage by reducing the cross-sectional area of the flow path in the cooling passage to improve the cooling capacity.
However, the smaller the cross-sectional area of the flow path, the higher the risk of the cooling passage being blocked by foreign matter.

In view of the above circumstances, at least one embodiment of the present disclosure aims to suppress the risk of blockage due to foreign matter in the cooling passage of the high temperature component.

(1) The high-temperature parts according to at least one embodiment of the present disclosure are
A plurality of first cooling passages extending in a straight line and
The extending direction of the first cooling passage so as to be separated from the first cooling passage in the perpendicular direction of the plane including the extending direction of the plurality of first cooling passages and communicate with any of the first cooling passages. With multiple second cooling passages extending along
With
The maximum cross-sectional area of each of the first cooling passages is larger than the maximum cross-sectional area of the second cooling passage closest to the first cooling passage in the cross section orthogonal to the extending direction.

(2) The rotary machine according to at least one embodiment of the present disclosure includes high-temperature parts having the configuration of (1) above.

According to at least one embodiment of the present disclosure, the risk of blockage due to foreign matter can be suppressed in the cooling passage of the high temperature component.

It is the schematic which shows the whole structure of the gas turbine as an example of a rotary machine. It is sectional drawing which shows the gas flow path of a gas turbine. It is a perspective view about one of the division bodies constituting the division ring which concerns on some embodiments. It is a perspective view about one of the division bodies constituting the division ring which concerns on some embodiments. It is sectional drawing in A arrow view of FIG. It is sectional drawing in B arrow view of FIG. It is an enlarged perspective view about a part of the divided body shown in FIG. It is sectional drawing in C arrow view of FIG. It is sectional drawing in D arrow view of FIG. It is a figure which shows one Embodiment of the cross section in E arrow view of FIG. It is a figure which shows the other embodiment of the cross section in E arrow view of FIG. It is a figure which shows a part of the CC arrow cross section of FIG. 5 about the divided body which concerns on some embodiments. It is a figure which shows a part about one Embodiment of the FF arrow cross section of FIG. It is a figure which shows a part about one Embodiment of the GG arrow cross section of FIG. It is a figure which shows a part about another embodiment of the FF arrow cross section of FIG. It is a graph which shows the state of the change of the cross-sectional area of the 1st cooling passage and the 2nd cooling passage by the position in the axial direction. It is a figure which also shows the graph which shows the relationship between the position in the axial direction and each value in the divided body which concerns on one Embodiment. It is a figure which shows a part about still another embodiment of the FF arrow cross section of FIG. It is a figure which shows a part about still another embodiment of the FF arrow cross section of FIG. It is a perspective view of a part of the axial Da upstream side of the divided body which concerns on some embodiments. It is a perspective view of a part of the axial Da upstream side of the divided body which concerns on some embodiments. It is a figure which shows an example of the shape of the flow path cross section of the 1st cooling passage or the 2nd cooling passage. It is a figure which shows an example of the shape of the flow path cross section of the 1st cooling passage or the 2nd cooling passage. It is a figure which shows a part about still another embodiment of the FF arrow cross section of FIG. It is a figure which shows a part about still another embodiment of the FF arrow cross section of FIG.

Hereinafter, some embodiments of the present disclosure will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described as embodiments or shown in the drawings are not intended to limit the scope of the present disclosure to this, and are merely explanatory examples. No.
For example, expressions that represent relative or absolute arrangements such as "in a certain direction", "along a certain direction", "parallel", "orthogonal", "center", "concentric" or "coaxial" are exact. Not only does it represent such an arrangement, but it also represents a state of relative displacement with tolerances or angles and distances to the extent that the same function can be obtained.
For example, expressions such as "same", "equal", and "homogeneous" that indicate that things are in the same state not only represent exactly the same state, but also have tolerances or differences to the extent that the same function can be obtained. It shall also represent the existing state.
For example, an expression representing a shape such as a quadrangular shape or a cylindrical shape not only represents a shape such as a quadrangular shape or a cylindrical shape in a geometrically strict sense, but also an uneven portion or chamfering within a range in which the same effect can be obtained. The shape including the part and the like shall also be represented.
On the other hand, the expressions "equipped", "equipped", "equipped", "included", or "have" one component are not exclusive expressions that exclude the existence of other components.

In the following description, high temperature parts according to some embodiments will be described by taking high temperature parts used in a gas turbine as an example.
FIG. 1 is a schematic view showing an overall configuration of a gas turbine 10 as an example of a rotary machine. FIG. 2 is a cross-sectional view showing a gas flow path of the gas turbine 10.

In the present embodiment, as shown in FIG. 1, the gas turbine 10 is configured such that a compressor 11, a combustor 12, and a turbine 13 are coaxially arranged by a rotor 14, and a generator 15 is provided at one end of the rotor 14. It is connected. In the following description, the direction in which the axis Ax of the rotor 14 extends is the axial Da, the circumferential direction around the axis of the rotor 14 is the circumferential Dc, and the direction perpendicular to the axis Ax of the rotor 14 is the diameter. Let the direction Dr.

The compressor 11 generates high-temperature and high-pressure compressed air AC by passing the air AI taken in from the air intake through a plurality of stationary blades and moving blades and compressing the air AI. The combustor 12 supplies a predetermined fuel FL to the compressed air AC and burns the compressed air AC to generate a high-temperature and high-pressure combustion gas FG. The turbine 13 drives and rotates the rotor 14 by passing the high-temperature and high-pressure combustion gas FG generated by the combustor 12 through the plurality of stationary blades and moving blades, and drives the generator 15 connected to the rotor 14. do.

Further, as shown in FIG. 2, in the turbine 13, the turbine stationary blade (static blade) 21 is configured such that the hub side of the airfoil portion 23 is fixed to the inner shroud 25 and the tip side is fixed to the outer shroud 27. There is. The turbine blade (moving blade) 41 is configured such that the base end portion of the airfoil portion 43 is fixed to the platform 45. Then, the outer shroud 27 and the split ring 50 arranged on the tip end side of the rotor blade 41 are supported by the vehicle interior (turbine vehicle interior) 30 via the heat shield ring 35, and the inner shroud 25 is supported by the support ring 31. Has been done. Therefore, the combustion gas flow path 32 through which the combustion gas FG passes is formed along the axial direction Da as a space surrounded by the inner shroud 25, the outer shroud 27, the platform 45, and the dividing ring 50.

The inner shroud 25, the outer shroud 27, and the dividing ring 50 function as gas path surface forming members. The gas path surface forming member has a gas path surface that partitions the combustion gas flow path 32 and is in contact with the combustion gas FG.

The combustor 12, the moving blade 41 (for example, the platform 45), the stationary blade 21 (for example, the inner shroud 25 and the outer shroud 27), the split ring 50, and the like are high-temperature components used in a high-temperature environment in which the combustion gas FG comes into contact. , Requires cooling with a cooling medium. In the following description, as an example of the cooling structure of the high temperature component, the cooling structure of the divided ring 50 of the gas turbine 10 in which a plurality of divided bodies 51 are arranged in an annular shape along the circumferential direction Dc will be described.

FIG. 3 is a perspective view of one of the divided bodies 51 constituting the divided ring 50 according to some embodiments.
FIG. 4 is a perspective view of one of the divided bodies 51 constituting the divided ring 50 according to some embodiments, and shows a state before attachment of the closing member 517, which will be described later.
FIG. 5 is a cross-sectional view taken along the line A of FIG.
FIG. 6 is a cross-sectional view taken along the line B of FIG.
FIG. 7 is an enlarged perspective view of a part of the divided body 51 shown in FIG.
FIG. 8 is a cross-sectional view taken along the line C of FIG.
FIG. 9 is a cross-sectional view taken along the line D of FIG.
FIG. 10 is a diagram showing an embodiment of a cross section in the direction of arrow E in FIG.
FIG. 11 is a diagram showing another embodiment of the cross section in the E arrow view of FIG.

(About the split body 51)
The split ring 50 according to some embodiments is composed of a plurality of split bodies 51 arranged in a ring shape in the circumferential direction Dc. As shown in FIGS. 3 to 7, each divided body 51 includes a plate-shaped main body portion 53 having a cooling passage 6 inside, and a protruding portion 55 provided so as to project from the main body portion 53. In the split body 51 according to some embodiments, the protruding portion 55 includes a protruding portion 55 on the upstream side of the axial Da and a protruding portion 55 on the downstream side of the axial Da.
In the divided body 51 according to some embodiments, the outer surface 532 on the outer side of the radial Dr of the main body 53 and the side surface 55a of the protrusion 55 on the downstream side of the axial Da facing the upstream side of the axial Da are connected. It is connected by 57.
In the split body 51 according to some embodiments, the protruding portion 55 is separated from the outer surface 532 of the main body portion 53 by an inlet opening 64a described later in the cooling passage 6.
In the divided body 51 according to some embodiments, the side surface 55a of the protrusion 55 on the downstream side of the axial Da facing the upstream side of the axial Da extends in the intersecting direction with respect to the outer surface 532 of the main body 53. Is.
In the split body 51 according to some embodiments, the connecting portion 57 is connected to one end 571 connected to the surface (outer surface 532) of the main body portion 53 and to the intersection surface (side surface 55a) of the protruding portion 55. It has the other end 573 and extends from one end 571 to the other end 573 across the inlet opening 64a described later.

As shown in FIG. 2, the divided body 51 is arranged so that the inner surface 531 inside the radial Dr of the main body 53 faces the combustion gas flow path 32 through which the combustion gas FG flows. A rotor blade 41 that rotates around the rotor 14 is arranged inside the main body 53 in the radial direction with a certain gap. In order to prevent thermal damage due to the high-temperature combustion gas FG, the main body 53 is formed with a plurality of axial passages (cooling passages) 6 extending in the axial direction Da.
A plurality of cooling passages 6 are arranged in parallel in the circumferential direction Dc.

Although not shown, in the gas turbine 10 according to one embodiment, cooling air CA is supplied to each of the divided bodies 51 according to some embodiments from the outer surface 532 side outside the radial Dr of the main body 53. It is configured as follows. The cooling air CA supplied to the split body 51 convectally cools the main body 53 of the split body 51 in the process of flowing through the cooling passage 6 and discharging it into the combustion gas FG.

In the split body 51 according to some embodiments, the protruding portion 55 constitutes a hook 59 for attaching the split body 51 to the vehicle interior 30 side of the gas turbine 10. For example, in the split body 51 according to some embodiments, as shown in FIG. 2, the claw portion 59a of the hook 59 engages with the heat shield ring 35 and is locked to the heat shield ring 35, thereby engaging the heat shield ring 35. It is supported by the passenger compartment (turbine passenger compartment) 30 via 35.

(About cooling passage 6)
Hereinafter, the cooling passage 6 according to some embodiments will be described.
For convenience of explanation regarding the cooling passage 6, it is assumed that the positions P1 to P5 in the axial direction Da are the respective positions shown in FIG. The positions P1 to P5 are sequentially located from the upstream side to the downstream side in the axial direction Da. For example, the position P1 is the position of the upstream side connection end portion 61a described later. Further, for example, the position P5 is the position of the downstream side connection end portion 61b described later.
The cooling passages 6 according to some embodiments extend along a plurality of first cooling passages 61 extending linearly in the axial direction Da and the extending direction (axial direction Da) of the first cooling passage 61. A plurality of second cooling passages 62 and an introduction passage 64 are included.

(First cooling passage 61)
Each of the plurality of first cooling passages 61 is arranged so as to be separated from each other in the circumferential direction Dc. The first cooling passages 61 adjacent to each other in the circumferential direction Dc are partitioned by the first partition wall 71.
Each of the plurality of first cooling passages 61 includes an upstream connection end portion 61a connected to the second cooling passage 62 via the first folding passage 66 described later.
Each of the plurality of first cooling passages 61 includes a downstream connection end portion 61b connected to the introduction passage 64 via the second folding passage 65 described later.
Each of the plurality of first cooling passages 61 is also referred to as a downstream passage 61.

(Second cooling passage 62)
Each of the plurality of second cooling passages 62 is separated from the first cooling passage 61 in the perpendicular direction (radial direction Dr) of the plane including the extending direction (axial direction Da) of the plurality of first cooling passages 61. It extends along the extending direction (axial direction Da) of the first cooling passage 61 so as to communicate with any of the cooling passages 61.
Each of the plurality of second cooling passages 62 is arranged so as to be separated from each other in the circumferential direction Dc. The second cooling passages 62 adjacent to each other in the circumferential direction Dc are partitioned by the second partition wall 72.

In the divided body 51 according to some embodiments, as shown in FIGS. 5 and 6, a plurality of second cooling passages 62 are arranged at the radial Dr position close to the inner surface 531 when viewed from the circumferential direction Dc. The plurality of first cooling passages 61 are arranged at the radial Dr position farther from the inner surface 531 than the plurality of second cooling passages 62.

As shown in FIGS. 5, 6 and 9, the end surface 71a on the downstream side of the axial direction Da of the first partition wall 71 may be an inclined surface inclined inward in the radial direction Dr, and is not shown. Although not, it may extend parallel to the radial Dr.

(1st turnaround passage 66)
In the divided body 51 according to some embodiments, one second cooling passage 62 is connected to one first cooling passage 61. Each of the first cooling passages 61 and the second cooling passage 62 communicating with the first cooling passage 61 are connected to each other by each of the plurality of first folding passages 66.
The plurality of first folding passages 66 are arranged near the end of the main body 53 on the upstream side of the axial Da, and the end of the first cooling passage 61 on the upstream side of the axial Da and the second cooling passage 62. It is connected to the end on the upstream side of the axial Da.
For example, as in one embodiment shown in FIG. 10, it is preferable that each of the plurality of first turn-back passages 66 is arranged so as to be separated from each other in the circumferential direction Dc. That is, it is preferable that the first folding passages 66 adjacent to each other in the circumferential direction Dc are partitioned by the folding passage partition wall 76.
Thereby, the first turn-back passages 66 adjacent to each other along the circumferential direction Dc can be separated from each other. Further, since the folding passage partition wall 76 functions as a heat transfer member to the cooling air CA flowing through the first folding passage 66, the cooling capacity can be improved.
In the following description, the first turn-back passage 66 is also referred to as an intermediate turn-back passage 66.

The first folding passage 66 does not have to be partitioned by the folding passage partition wall 76, and the first folding passage 66 may be one header space as in another embodiment shown in FIG. 11, for example. An intermediate header portion 66A may be provided.

(Introduction passage 64)
As shown in FIGS. 3 to 8, the split body 51 according to some embodiments includes an introduction passage 64. The introduction passage 64 extends the first cooling passage 61 so as to be separated from the first cooling passage 61 on the side opposite to the plurality of second cooling passages 62 in the radial direction and communicate with the plurality of first cooling passages 61, respectively. It extends along the existing direction (axial direction Da) and the plate width direction (circumferential direction Dc) of the main body 53.
In the divided body 51 according to some embodiments, as shown in FIG. 8, the passage width along the circumferential direction Dc of the introduction passage 64 is along the circumferential direction Dc circumferential direction Dc of the plurality of first cooling passages 61. Substantially equal to the placement range. That is, in the divided body 51 according to some embodiments, the introduction passage 64 is one passage not separated by the circumferential direction Dc.
The introduction passage 64 is also referred to as an upstream passage 64.

An inlet opening 64a is formed at the end of the introduction passage 64 on the upstream side in the axial direction Da. The inlet opening 64a is a slit opening extending along the plate width direction (circumferential direction Dc) of the main body 53.
In the divided body 51 according to some embodiments, as described above, the protruding portion 55 on the downstream side of the axial Da is separated from the outer surface 532 of the main body portion 53 by the inlet opening 64a.

(2nd turnaround passage 65)
In the split body 51 according to some embodiments, the introduction passage 64 and the plurality of first cooling passages 61 are connected by a second folding passage 65.
In the split body 51 according to some embodiments, the second folding passage 65 is arranged near the end of the main body 53 on the downstream side of the axial Da, and the end of the introduction passage 64 on the downstream side of the axial Da. Is connected to the end of the first cooling passage 61 on the downstream side in the axial direction Da.
In the following description, the second turn-back passage 65 is also referred to as an entrance-side turn-back passage 65.

(Header section 80 on the exit side)
The split body 51 according to some embodiments includes a plurality of outlet side header portions 80. In the split body 51 according to some embodiments, each of the plurality of second cooling passages 62 has an end portion on the downstream side of the axial Da connected to any one of the plurality of outlet side header portions 80. In the split body 51 according to some embodiments, a plurality of second cooling passages 62 are connected to one outlet side header portion 80. In the example shown in FIG. 10, the ends of the six second cooling passages 62 adjacent to each other in the circumferential direction Dc are connected to the upstream side of the axial Da of one outlet side header portion 80. In some embodiments, the split 51 is formed with a plurality of outlet side headers 80.

1 for discharging the cooling air CA flowing into the outlet side header 80 to the outside of the outlet side header 80, that is, to the outside of the divided body 51, on the inner wall 82 on the downstream side of the axial Da of each outlet side header 80. Two exit passages 83 are formed. The outlet passage 83 opens into the combustion gas FG at the downstream end portion 511 of the axial direction Da in the split body 51.

(Flow of cooling air CA)
In the split body 51 according to some embodiments, the cooling air CA supplied from the outside of the split body 51 to the outer surface 532 side of the radial Dr outside of the main body 53 is introduced from the inlet opening 64a of the introduction passage 64. It flows into 64 and circulates in the introduction passage 64 toward the downstream side of Da in the axial direction.
The cooling air CA that has flowed through the introduction passage 64 flows into each of the first cooling passages 61 through the inlet side turn-back passage 65, and flows through each of the first cooling passages 61 toward the upstream side of Da in the axial direction.
The cooling air CA that has flowed through each of the first cooling passages 61 flows into each of the second cooling passages 62 through the intermediate folding passage 66 and flows through each of the second cooling passages 62 toward the downstream side of Da in the axial direction. do.
The cooling air CA flowing through each of the second cooling passages 62 is collected by each outlet side header portion 80 and discharged from the outlet passage 83 to the outside of the divided body 51.

(About the risk of blockage of the cooling passage)
In a machine operated by a high-temperature working gas such as a gas turbine 10, generally, the removal of heat by cooling leads to a decrease in the thermal efficiency of the machine. Therefore, it is desirable to efficiently cool high-temperature parts with as few cooling media as possible. Therefore, by reducing the cross-sectional area of the flow path in the cooling passage, that is, the cross-sectional area of the cooling passage appearing in the cross section orthogonal to the extending direction of the cooling passage, the flow rate of the cooling medium in the cooling passage is increased and the cooling capacity is improved. Is desirable.
However, the smaller the cross-sectional area of the flow path, the higher the risk of the cooling passage being blocked by foreign matter.

In the conventional split body, generally, the cooling passages are singly arranged at one radial Dr position near the combustion gas flow path 32 through which the combustion gas FG flows.
On the other hand, in the split body 51 according to some embodiments, in order to suppress the risk of blockage of the cooling passage, the flow path cross-sectional area of the second cooling passage 62 is made larger than that of the cooling passage in the conventional split body. There is. Then, in the split body 51 according to some embodiments, the flow velocity of the cooling air CA is larger than that of the conventional split body by making the flow path cross-sectional area of the second cooling passage 62 larger than that of the cooling passage in the conventional split body. The first cooling passage 61 is arranged outside the radial Dr of the second cooling passage 62 in order to compensate for the cooling capacity that is reduced due to the reduction. That is, in the divided body 51 according to some embodiments, the cooling passages 6 are doubly arranged in the radial direction Dr.
As a result, the cross-sectional area of the cooling passage 6 can be increased while ensuring the cooling capacity as compared with the case where only one of the plurality of first cooling passages 61 or the plurality of second cooling passages 62 is provided. Therefore, the cooling capacity is compared with the case where only one of the plurality of first cooling passages 61 or the plurality of second cooling passages 62 is provided, that is, the case where the cooling passages are arranged in a single layer as in the conventional divided body. The risk of blockage in the cooling passage 6 can be suppressed while ensuring the above.
Further, the reliability of the gas turbine 10 can be improved by using the divided body 51 according to some embodiments.

(About the cross-sectional area of the cooling passage 6)
FIG. 12 is a diagram showing a part of a cross section taken along the line CC of FIG. 5 for the divided body 51 according to some embodiments.
FIG. 13 is a diagram showing a part of an embodiment of the FF arrow cross section of FIG.
FIG. 14 is a diagram showing a part of an embodiment of the cross section taken along the line GG of FIG.
FIG. 15 is a diagram showing a part of another embodiment of the FF arrow cross section of FIG.
FIG. 16 is a graph showing how the cross-sectional areas of the first cooling passage 61 and the second cooling passage 62 change depending on the position of the axial Da.
FIG. 17 shows the relationship between the position of the axial Da and the temperature Ta of the cooling air CA, the relationship between the position of the axial Da and the cross-sectional area S of the cooling passage 6, and the axial Da in the divided body 51 according to the embodiment. It is a figure which also shows the relationship between the position of and the heat transfer coefficient hc on the cooling side, and the relationship between the position of Da in the axial direction and the heat transfer coefficient hg on the combustion gas side, respectively.

The axial Da position of the CC arrow cross section in FIG. 5 is, for example, a position between the position P4 and the position P5, and the introduction passage 64, the first cooling passage 61, and the second cooling passage 62 are arranged in the radial direction Dr. Is the stacked position.
The axial Da position of the FF arrow cross section in FIG. 5 is, for example, a position between the position P3 and the position P4, and the first cooling passage 61 and the second cooling passage 62 are laminated in the radial direction Dr. The position.
The axial Da position of the cross section taken along the line GG in FIG. 5 is, for example, a position between the positions P1 and P2, and the first cooling passage 61 and the second cooling passage 62 are laminated in the radial direction Dr. The position.

For convenience of illustration, the graph shows that the cross-sectional area S1 of the first cooling passage 61 is larger than the cross-sectional area S2 of the second cooling passage 62 in the section from the position P4 to the position P5 in the axial direction Da in FIG. However, the cross-sectional area S1 of the first cooling passage 61 and the cross-sectional area S2 of the second cooling passage 62 may be equal.

For example, as shown in FIG. 16, in some embodiments, the first cooling passage 61 is configured such that the cross-sectional area S1 increases from the downstream side to the upstream side in the axial direction Da. Further, as shown in FIG. 16, for example, in some embodiments, the cross-sectional area S1 of the first cooling passage 61 is a disconnection of the first cooling passage 61 at least in the section from the position P1 to the position P4 in the axial direction Da. The area S1 is larger than the cross-sectional area S2 of the second cooling passage 62.
As a result, the flow velocity of the cooling air CA in the first cooling passage 61 can be suppressed and the static pressure can be increased. Therefore, since the static pressure in the first cooling passage 61 located on the upstream side of the second cooling passage 62 with respect to the flow direction of the cooling air CA can be improved, the flow velocity of the cooling air CA in the second cooling passage 62 can be increased. , The cooling capacity in the second cooling passage 62 can be improved.
Further, the sum of the pressure losses between the first cooling passage and the second cooling passage can be reduced as compared with the case where the cross-sectional area S1 of the first cooling passage 61 is equal to the cross-sectional area S2 of the second cooling passage 62.
In some embodiments, the flow path cross-sectional dimension of the second cooling passage 62, that is, the dimension in the direction orthogonal to the axial direction Da, has a diameter of 0 if the flow path cross section of the second cooling passage 62 is circular. If the flow path cross section of the second cooling passage 62 is rectangular, the length of one side is 0.1 mm or more and 2.0 mm or less.

For example, as shown in FIG. 16, in some embodiments, the cross-sectional area S1 of the first cooling passage 61 may be constant from position P5 to position P4. The cross-sectional area S1 of the first cooling passage 61 may be monotonically increased from the position P4 to the position P3. The cross-sectional area S1 of the first cooling passage 61 may be monotonically increased from the position P3 to the position P2. The cross-sectional area S1 of the first cooling passage 61 may be constant from the position P2 to the position P1.
The rate at which the cross-sectional area S1 increases from the position P3 to the position P2 may be larger than the rate at which the cross-sectional area S1 increases from the position P4 to the position P3.

Further, as shown by the broken line a1 in FIG. 16, for example, the cross-sectional area S1 of the first cooling passage 61 may be monotonically increased at a constant rate of increase from the position P4 to the position P2.
As shown by the broken line a2 in FIG. 16, for example, the cross-sectional area S2 of the second cooling passage 62 decreases from the position P1 to an arbitrary position on the axial Da downstream side of the position P1 toward the downstream side. You may.

With reference to FIG. 17, the relationship between the temperature Ta of the cooling air CA, the cross-sectional area S of the cooling passage 6, the heat transfer coefficient hb on the main body side and the heat transfer coefficient hg on the combustion gas side, and the position in the axial direction Da will be described. .. The heat transfer coefficient hc on the cooling side is the heat transfer coefficient between the cooling air CA and the wall portion forming the cooling passage 6, and the heat transfer coefficient hg on the combustion gas side is the heat transfer coefficient between the combustion gas FG and the main body 53. The heat transfer coefficient between them.
In the graph of FIG. 17, in order to explain the tendency of change of each value, the tendency of change of each value is simplified.

Of the temperature Ta of the cooling air CA, the temperature Ta1 of the cooling air CA in the first cooling passage 61 rises from the downstream side of the axial Da to the upstream side. The temperature Ta2 of the cooling air CA in the second cooling passage 62 rises from the upstream side to the downstream side of the axial Da.

Of the cross-sectional area S of the cooling passage 6, the cross-sectional area S1 of the first cooling passage 61 tends to increase from the downstream side in the axial direction Da to the upstream side as described above. As described above, the cross-sectional area S2 of the second cooling passage 62 is constant regardless of the axial Da position.

Since the cross-sectional area S1 of the first cooling passage 61 tends to increase from the downstream side of the axial Da to the upstream side, the flow velocity of the cooling air CA in the first cooling passage 61 tends to increase from the downstream side of the axial Da to the upstream side. It tends to decrease as it goes.
Therefore, of the cooling-side heat transfer coefficient hc, the heat transfer coefficient hc1 between the cooling air CA and the wall portion forming the first cooling passage 61 tends to decrease from the downstream side to the upstream side in the axial direction Da.
The heat transfer coefficient hc2 between the cooling air CA and the wall portion forming the second cooling passage 62 is constant regardless of the axial Da position.

The heat transfer coefficient hg on the combustion gas side is higher at the axial Da position facing the tip of the rotor blade 41 than at other positions.

(Relationship between cross-sectional area S1 and cross-sectional area S2)
In the divided body 51 according to some embodiments, the cross-sectional area (flow path area) of the cooling passage 6 is set in consideration of the tendency of the change of each value shown in FIG.
For example, in the divided body 51 according to some embodiments, the maximum value S1max of the cross-sectional area S1 of each first cooling passage 61 is within the cross section orthogonal to the extending direction (axial direction Da) of the first cooling passage 61. It is preferable that the cross-sectional area S2 of the second cooling passage 62 closest to the first cooling passage 61 is larger than the maximum value S2max.
Expressing this by an equation, it becomes the following equation (1).
S2max <S1max ... (1)

As a result, the maximum value S1max of the cross-sectional area S1 of each first cooling passage 61 is the maximum value of the cross-sectional area S2 of the second cooling passage 62 closest to the first cooling passage 61 in the cross section orthogonal to the axial direction Da. Compared with the case where it is the same as or smaller than S2max, the flow velocity of the cooling air CA in the first cooling passage 61 can be suppressed and the static pressure can be increased. Therefore, since the static pressure in the first cooling passage 61 located on the upstream side of the second cooling passage 62 with respect to the flow direction of the cooling air CA can be improved, the flow velocity of the cooling air CA in the second cooling passage 62 can be increased. , The cooling capacity in the second cooling passage 62 can be improved.
Further, the reliability of the gas turbine 10 can be improved by using the divided body 51 according to some embodiments.

In the divided body 51 according to some embodiments, the maximum value S1max of the cross-sectional area S1 of each first cooling passage 61 is the maximum of the total cross-sectional area AS2 of the second cooling passage 62 communicating with the first cooling passage 61. It should be larger than the value AS2max.
Expressing this by an equation, it becomes the following equation (2).
AS2max <S1max ... (2)
The total cross-sectional area AS2 is the sum of the cross-sectional areas S2 of all the second cooling passages 62 communicating with the first cooling passage 61.

As a result, the maximum value S1max of the cross-sectional area S1 of each first cooling passage 61 is equal to or smaller than the maximum value AS2max of the total cross-sectional area AS2 of the second cooling passage 62 communicating with the first cooling passage 61. Therefore, the flow velocity of the cooling air CA in the first cooling passage 61 can be suppressed to increase the static pressure. Therefore, since the static pressure in the first cooling passage 61 located on the upstream side of the second cooling passage 62 with respect to the flow direction of the cooling air CA can be improved, the flow velocity of the cooling air CA in the second cooling passage 62 can be increased. , The cooling capacity in the second cooling passage 62 can be improved.

In order to satisfy the above-mentioned formula (1) or formula (2), for example, as shown in FIGS. 13 and 14, the dimension H1 of each first cooling passage 61 in the radial direction Dr is set to each second in the radial direction Dr. The dimension H2 of the cooling passage 62 may be made larger than that. For example, the maximum value H1max of the dimension H1 of each first cooling passage 61 in the radial direction Dr is larger than the maximum value H2max of the dimension H2 in the radial direction Dr of the second cooling passage 62 communicating with the first cooling passage 61. You may.
In the split body 51 according to some embodiments, for example, from the upstream side connection end portion 61a to a position separated to the downstream side of the axial direction Da by a distance of 0.5 times the length of the axial direction Da of the first cooling passage 61. At any axial Da position in the section, the maximum value H1max of the dimension H1 of each first cooling passage 61 is the dimension H2 in the radial direction Dr of the second cooling passage 62 communicating with the first cooling passage 61. It should be larger than the maximum value H2max.
The length of the first cooling passage 61 in the axial direction Da is, for example, the length from the downstream connection end 61b to the upstream connection end 61a.

Further, in order to satisfy the above-mentioned formula (1) or formula (2), for example, as shown in FIG. 15, each first cooling in the passage width direction (circumferential direction Dc) orthogonal to the radial direction Dr and the axial direction Da. The dimension W1 of the passage 61 may be made larger than the dimension W2 of each second cooling passage 62 in the passage width direction. For example, the maximum value W1max of the dimension W1 of each first cooling passage 61 in the passage width direction is larger than the maximum value W2max of the dimension W2 in the passage width direction of the second cooling passage 62 communicating with the first cooling passage 61. You may.
In the split body 51 according to some embodiments, for example, from the upstream side connection end portion 61a to a position separated to the downstream side of the axial direction Da by a distance of 0.5 times the length of the axial direction Da of the first cooling passage 61. At any axial Da position in the section, the maximum value W1max of the dimension W1 of each first cooling passage 61 is the dimension W2 in the passage width direction of the second cooling passage 62 communicating with the first cooling passage 61. It should be larger than the maximum value W2max.

In the divided body 51 according to some embodiments, each first cooling passage 61 has a cross-sectional area S1 in a region on the connection end portion (upstream side connection end portion) 61a side, which is upstream of the connection end portion. It is preferable that it is larger than the cross-sectional area S1 in the region far from 61a.
As a result, in each of the first cooling passages 61, the cross-sectional area S1 becomes larger in the region closer to the second cooling passage 62. Therefore, of the first cooling passage 61 located on the upstream side of the second cooling passage 62 with respect to the flow direction of the cooling air CA, the static pressure in the region closer to the second cooling passage 62 can be improved, so that the second cooling passage 62 can be improved. The flow velocity of the cooling air CA in the cooling passage 62 can be efficiently increased, and the cooling capacity in the second cooling passage 62 can be efficiently improved.
In the divided body 51 according to some embodiments, there may be a cooling passage 6 that does not satisfy the above-mentioned formula (1) or formula (2).

(Relationship between the circumferential direction Dc positions of the first cooling passage 61 and the second cooling passage 62)
For example, as shown in FIGS. 8, 12 to 15, each circumferential Dc position of the second cooling passage 62 is substantially the same as each circumferential Dc position of the first cooling passage 61. That is, in the divided body 51 according to some embodiments, the first partition wall 71 is substantially the same position as the second partition wall 72 in the passage width direction (circumferential direction Dc) when viewed from the radial direction Dr. It should be placed in.
Thereby, the structure of the connecting portion between the first cooling passage 61 and the second cooling passage 62, that is, the intermediate folding passage 66 can be simplified.
It should be noted that, not all of the plurality of second cooling passages 62, but at least one or more circumferential Dc positions may be substantially the same as any of the plurality of first cooling passages 61 in the circumferential direction Dc position. ..

FIG. 18 is a diagram showing a part of still another embodiment of the FF arrow cross section of FIG. For example, as shown in FIG. 18, each circumferential Dc position of the second cooling passage 62 may be substantially different from each circumferential Dc position of the first cooling passage 61. That is, in the divided body 51 according to still another embodiment, the first partition wall 71 is substantially different from the second partition wall 72 in the passage width direction (circumferential direction Dc) when viewed from the radial direction Dr. It may be arranged in.
As a result, when viewed from the radial direction Dr, the first partition wall 71 and the second partition wall 72 are viewed from the radial direction Dr as compared with the case where the first partition wall 71 and the second partition wall 72 are arranged at substantially the same position in the circumferential direction Dc. Occasionally, the area where the second partition wall 72 and the first cooling passage 61 overlap increases. As a result, for example, the heat transmitted between the two adjacent second cooling passages 62 through the second partition wall 72 is easily transferred to the cooling air CA flowing through the first cooling passage 61.
It should be noted that, not all of the plurality of second cooling passages 62, but at least one or more circumferential Dc positions may be substantially different from any of the plurality of first cooling passages 61 in the circumferential direction Dc position.

(Number of first cooling passages 61 and second cooling passages 62)
FIG. 19 is a diagram showing a part of still another embodiment of the FF arrow cross section of FIG. In the embodiment shown in FIG. 19, at the axial Da position of the cross section taken along the line FF in FIG. 5, the dimension W1 of the circumferential direction Dc of one first cooling passage 61 is the circumferential direction of one second cooling passage 62. It is more than twice the size W2 of Dc.
For example, in the embodiment shown in FIG. 19, two second cooling passages 62 may be connected to one first cooling passage 61.
That is, in the divided body 51 according to some of the above-described embodiments, one second cooling passage 62 is connected to one first cooling passage 61, but one first cooling passage 62 is connected. Two or more second cooling passages 62 may be connected to 61.

(About the opening formed at the end on the upstream side of Da in the axial direction)
FIG. 20 is a perspective view of a part of the split body 51 according to some embodiments on the upstream side in the axial direction Da, and shows a state before the closing member 517, which will be described later, is attached.
FIG. 21 is a perspective view of a part of the split body 51 according to some embodiments on the upstream side in the axial direction Da, and shows a state after the closing member 517, which will be described later, is attached.
In the split body 51 according to some embodiments, as shown in FIG. 20, an opening 515 facing the intermediate folding passage 66 is formed at the upstream end portion 513 on the upstream side in the axial direction Da. In the split body 51 according to some embodiments, the opening 515 is closed by the closing member 517.

In the split body 51 according to some embodiments, a pin gauge or the like (not shown) is passed through the opening 515 and the intermediate folding passage 66 before being closed by the closing member 517 from the outside of the split body 51 to the first cooling passage 61 or the first cooling passage 61. 2 Can be inserted into the cooling passage 62. Thereby, it can be confirmed that the first cooling passage 61 and the second cooling passage 62 are not blocked. It should be noted that it is visually confirmed that the first cooling passage 61 and the second cooling passage 62 are not blocked from the outside of the divided body 51 through the opening 515 and the intermediate folding passage 66 before being closed by the closing member 517. You can also.
In this way, after it is confirmed that the first cooling passage 61 and the second cooling passage 62 are not blocked, the closing member 517 is arranged in the opening 515 and closed. The closing member 517 can be fixed to the divided body 51 by welding or the like, for example.

In the split 51 according to some embodiments, the closing member 517 abuts at least a portion of the folded passage partition wall 76. More specifically, in the split body 51 according to some embodiments, the end face of the closing member 517 facing the axial Da downstream side is the end face of the plurality of folded passage partition walls 76 facing the axial Da upstream side. Contact at least part of.
As a result, leakage of the cooling air CA between the intermediate folding passages 66 adjacent to each other in the circumferential direction Dc across the folding passage partition wall 76 can be suppressed.
Further, when the closing member 517 comes into contact with at least a part of the folded passage partition wall 76, the closing member 517 can be easily positioned in the opening 515 when the closing member 517 is attached to the opening 515.

Since the divided body 51 according to some embodiments includes an opening 515 facing the plurality of intermediate folding passages 66 and a closing member 517 that closes the opening 515, the opening 515 is passed through the intermediate folding passage 66. The first cooling passage 61 and the second cooling passage 62 can be accessed. Thereby, for example, it can be confirmed whether or not the first cooling passage 61 and the second cooling passage 62 have a specified opening area at the manufacturing stage of the divided body 51, which contributes to the quality control of the divided body 51.

(About the position of the intermediate turn-back passage 66)
For example, as shown in FIG. 5, in the split body 51 according to some embodiments, at least a part of the plurality of intermediate folding passages 66 is an upstream end portion which is one end face in the axial direction Da of the split body 51. It is preferable that the distance from the upstream end surface 513a of the 513 is within twice the passage height H6 of the intermediate folding passage 66 in the radial direction Dr. That is, in the divided body 51 according to some embodiments, the thickness Lu of the upstream end portion 513 located on the axial Da upstream side of the intermediate folding passage 66 is twice the passage height H6 of the intermediate folding passage 66. It is preferable that it is within (Lu ≦ 2 × H6).

In the intermediate turn-back passage 66, since the first cooling passage 61 and the second cooling passage 62 having different positions in the radial direction are connected, the direction of the flow of the cooling air CA changes. Therefore, the cooling air CA in the intermediate turn-back passage 66 The heat transfer coefficient to is improved. Therefore, the cooling capacity of the region near the intermediate folding passage 66 in the divided body 51 is improved.
Generally, in the vicinity of the upstream end surface 513a of the split body 51, the heat load is higher than in other regions, so it is desirable to arrange the intermediate folding passage 66 in the vicinity of the upstream end surface 513a. By arranging the intermediate folding passage 66 in the vicinity of the upstream end surface 513a, the vicinity of the upstream end surface 513a in the split body 51 can be efficiently cooled.

(About the position of the entrance side turnaround passage 65)
For example, as shown in FIG. 5, in the split body 51 according to some embodiments, at least a part of the inlet side folding passage 65 is the downstream end portion 511 which is the other end face in the axial direction Da in the split body 51. It is preferable that the vehicle exists at a distance within 3 times the passage height H5 of the inlet-side folding passage 65 in the radial direction from the downstream end surface 511a of the above. That is, in the divided body 51 according to some embodiments, the thickness Ld of the downstream end portion 511 located on the downstream side of the axial direction Da of the entrance side folding passage 65 is the passage height H5 of the entrance side folding passage 65. It is preferable that it is within 3 times (Ld ≦ 3 × H5).

In the inlet side return passage 65, since the introduction passage 64 and the first cooling passage 61 having different positions in the radial direction are connected, the direction of the flow of the cooling air CA changes. Therefore, the cooling air CA in the inlet side return passage 65 The heat transfer coefficient to is improved. Therefore, the cooling capacity of the region in the vicinity of the inlet-side folding passage 65 in the divided body 51 is improved.
Generally, in the vicinity of the downstream end surface 511a of the split body 51, the heat load is higher than in other regions due to the entrainment of the combustion gas FG. Therefore, it is desirable to arrange the inlet side folding passage 65 in the vicinity of the downstream end surface 511a. By arranging the inlet side folding passage 65 in the vicinity of the downstream end surface 511a, the vicinity of the downstream end surface 511a in the split body 51 can be efficiently cooled.

(Three-dimensional laminated model)
The divided body 51 according to some embodiments may be a three-dimensional laminated model formed by three-dimensional laminated modeling.
As a result, even a split body 51 provided with an elongated cooling passage 6 that is difficult to process by electric discharge machining can be obtained as a three-dimensional laminated model.

(About connection part 57)
Hereinafter, the role of the connecting portion 57 in the divided body 51 according to some embodiments will be described.
In the split body 51 according to some embodiments, the connecting portion 57 is a rib-shaped portion.
In the split body 51 according to some embodiments, as described above, the inlet opening 64a is a slit opening extending along the plate width direction (circumferential direction Dc) of the main body 53. A plurality of connecting portions 57 are provided within the formation range of the slit openings in the plate width direction (circumferential direction Dc).

In the divided body 51 according to some embodiments, since the protruding portion 55 is separated from the outer surface 532 of the main body portion 53 by the inlet opening 64a of the cooling passage 6, the temperature difference between the main body portion 53 and the protruding portion 55 is large. Where there is a tendency to expand, since the main body 53 and the protruding portion 55 are connected by the connecting portion 57, the connecting portion 57 functions as a heat transfer path and suppresses the temperature difference between the main body 53 and the protruding portion 55. can. As a result, the thermal stress at the protruding portion 55 can be suppressed.
Further, by connecting the protruding portion 55 and the main body portion 53 with the connecting portion 57, the deformation of the divided body 51 can be suppressed.
In the split body 51 according to some embodiments, the portion forming the inlet opening 64a can be reinforced by the plurality of connecting portions 57.

In the divided body 51 according to some embodiments, the radial direction of the protruding portion 55 is continuous from the side surface 55a (hereinafter, simply referred to as the side surface 55a) facing the axial direction Da upstream side of the protruding portion 55 on the downstream side of the axial direction Da. The surface facing the inside of Dr is an inclined surface (protruding portion inclined surface) 55b toward the inside of Dr in the radial direction toward the downstream side of Da in the axial direction. In the divided body 51 according to some embodiments, the position Pin in the axial direction Da where the intersection 55c of the side surface 55a and the inclined surface 55b of the protrusion and the outer surface 532 of the main body 53 face each other is the axial direction of the introduction passage 64. Since it is the end on the upstream side of Da, the axial Da position is the inlet end 641 of the introduction passage 64.

In the split body 51 according to some embodiments, as shown in FIG. 5, a part of the connecting portion 57 is located on the downstream side of Da in the axial direction from the inlet end 641 of the introduction passage 64. That is, in the divided body 51 according to some embodiments, the connecting portion 57 is arranged so that the invading portion 575, which is a part of the connecting portion 57, invades the inside of the cooling passage 6.
In the split body 51 according to some embodiments, the intruding portion 575 is connected to the protruding portion inclined surface 55b. That is, in the divided body 51 according to some embodiments, a part of the connecting portion 57 is connected to the protruding portion inclined surface 55b which is the forming wall surface of the cooling passage 6 connected to the intersecting surface (side surface 55a) of the protruding portion 55. ing.
As a result, the connection region between the protruding portion 55 and the connecting portion 57 can be secured in a region other than the intersection surface (side surface 55a), and the temperature difference between the main body portion 53 and the protruding portion 55 can be further suppressed.

In the split body 51 according to some embodiments, as shown in FIG. 5, the surface of the intrusion portion 575 facing inward in the radial direction is an inclined surface (outward in the radial direction Dr) toward the downstream side of the axial Da. Intrusion portion inclined surface) 575a. The intruding portion inclined surface 575a is separated from the outer surface 532. That is, at least a part of the invading portion 575 is separated from the outer surface 532.
Therefore, as compared with the case where the intrusion portion inclined surface 575a is connected to the outer surface 532, the partial volume in which the intrusion portion 575 invades into the introduction passage 64 can be suppressed, so that the flow path of the introduction passage 64 in the vicinity of the inlet opening 64a The decrease in area can be suppressed. Therefore, it is possible to suppress an increase in the flow velocity of the cooling air CA flowing through the introduction passage 64 in the vicinity of the inlet opening 64a, and to suppress a pressure loss in the introduction passage 64.
Further, since it is possible to suppress an increase in the flow velocity of the cooling air CA flowing through the introduction passage 64 in the vicinity of the inlet opening 64a, it is possible to prevent the protruding portion 55 from being excessively cooled, and the main body portion 53 and the protruding portion 55 The temperature difference can be further suppressed.
Further, since the protrusion 55 can be suppressed from being excessively cooled, the temperature rise of the cooling air CA in the introduction passage 64 can be suppressed, and the decrease in the cooling capacity in the first cooling passage 61 and the second cooling passage 62 can be suppressed. ..

(Regarding the relationship between the outer surface 532 and the cooling passage 6)
In the divided body 51 according to some embodiments, a part of the outer surface 532 of the main body 53 constitutes a part of the cooling passage 6. More specifically, in the split body 51 according to some embodiments, the cooling passage 6 is separated from the upstream passage (introduction passage 64) including the inlet opening 64a and the upstream passage 64 in the above-mentioned crossing direction. It includes a downstream passage (first cooling passage 61) arranged at a position, and an inlet side folding passage 65 which is a folding passage connecting the upstream passage 64 and the downstream passage 61. As shown in FIG. 5, a part of the outer surface 532 of the main body 53 constitutes a part of the upstream passage 64 and is connected to the forming wall surface 65a of the entrance side folded passage 65.

As a result, the cooling air CA easily flows into the cooling passage 6 along the outer surface 532 of the main body 53.
Further, the inlet opening 64a is on the other side (upstream side of the axial Da) from the end (downstream end 511) of the main body 53 on one side (downstream side of the axial Da) along the outer surface 532 of the main body 53. The cooling air CA flowing in from the inlet opening 64a can be guided to the downstream side of the axial Da by the upstream passage 64, and the cooling air CA can be guided to the inlet side folding passage even if the cooling air CA is provided at a position away from the inlet side. By guiding the cooling air CA to the downstream passage 61 via the 65, the cooling air CA can be guided from the inlet side folded passage 65 toward the upstream side of the axial Da.

(About the upstream inclined surface 577 of the connecting portion 57)
In the split body 51 according to some embodiments, the connecting portion 57 is an upstream inclined surface which is an inclined surface extending obliquely from one end 571 toward the other end 573 side with respect to the outer surface 532 of the main body 53. Has 577.
The upstream-side inclined surface 577 extends from one end 571 on the upstream side in the axial direction Da to the claw portion 59a of the hook 59, and is an inclined surface extending outward in the radial direction Dr toward the downstream side in the axial direction Da. be.

In the split body 51 according to some embodiments, the main body extends from one end 571 where the upstream inclined surface 577 is connected to the outer surface 532 of the main body 53 to the claw portion 59a of the hook 59 located radially outside the protruding portion 55. Since it extends diagonally with respect to the outer surface 532 of the portion 53, the connecting portion 57 becomes wider at the hem from the tip end side (diameter direction Dr outside) to the base end side (diameter direction Dr inside) of the protrusion portion 55. It will have a shape. Therefore, the area of the connecting portion between one end 571 of the connecting portion 57 and the outer surface 532 of the main body portion 53 can be increased, the amount of heat transfer from the main body portion 53 to the protruding portion can be increased, and the main body portion 53 and the protruding portion can be increased. The temperature difference from 55 can be further suppressed.

Further, since the upstream inclined surface 577 is an inclined surface toward the outside of the radial Dr as it goes toward the downstream side of the axial Da, for example, when the divided body 51 according to some embodiments is formed by three-dimensional laminated molding, it is laminated. If the direction is from the upstream side to the downstream side along the axial direction Da, the connecting portion 57 becomes a portion whose size along the radial direction gradually increases as the modeling proceeds. Therefore, the connecting portion 57 can be formed without forming the support, and the connecting portion 57 itself serves as a support for the protruding portion 55. Therefore, the number of supports to be formed can be reduced, the time required for the laminated molding can be shortened, and the process of removing the supports can be simplified.

Further, as described above, the connecting portion 57 becomes a portion whose size gradually increases along the radial direction as the molding proceeds, so that the protruding portion 55 has a shape when molding along the stacking direction. It is possible to alleviate sudden changes. Generally, in metal lamination molding, if there is a sudden change portion whose shape changes suddenly when molding along the lamination direction, the outer edge of the modeled object appearing in a cross section orthogonal to the lamination direction in the vicinity of the sudden change portion. The position may shift in the direction orthogonal to the stacking direction.
As described above, since the connecting portion 57 can alleviate the sudden change in shape of the protruding portion 55 when molding along the stacking direction, the shape of the divided body 51 is distorted in the vicinity of the protruding portion 55. It can be suppressed that it ends up.

(Regarding the shape of the flow path cross section of the first cooling passage 61 and the second cooling passage 62)
In some of the above-described embodiments, the shape of the flow path cross section of the first cooling passage 61 and the second cooling passage 62 is rectangular, but it may be circular or elliptical. Further, the shape of the flow path cross section of the first cooling passage 61 and the second cooling passage 62 may be a polygon other than a rectangle, or may be a combination of a polygon and a circle or an ellipse.
For example, the shape of the flow path cross section of the first cooling passage 61 and the shape of the flow path cross section of the second cooling passage 62 may be different. For example, the shape of the flow path cross section of the first cooling passage 61 may be circular, and the shape of the flow path cross section of the second cooling passage 62 may be polygonal. Further, for example, the shapes of the flow path cross sections of all the first cooling passages 61 do not have to be the same, but may be different. Similarly, the shape of the flow path cross section of all the second cooling passages 62 does not have to be the same, but may be different.

FIG. 22A is a diagram showing an example of a polygon other than a regular polygon as an example of the shape of the flow path cross section of the first cooling passage 61 or the second cooling passage 62.
FIG. 22B is a diagram showing an example of a shape in which a polygon and a circle are combined as an example of the shape of the flow path cross section of the first cooling passage 61 or the second cooling passage 62.
For example, the shape of the flow path cross section shown in FIGS. 22A and 22B has an inclined surface 601 inclined in the vertical direction shown on the upper side of the flow path.
For example, when the divided body 51 is formed by three-dimensional laminated molding, if the stacking direction in the cooling passage 6 is from the lower side to the upper side in the drawing, the cooling passage 6 has an inclined surface 601 as shown in FIGS. 22A and 22B, for example. If it has, it is possible to suppress the shape collapse of the inclined surface 601 which becomes an overhang region at the time of modeling.

FIG. 23A is a diagram showing a part of still another embodiment of the FF arrow cross section of FIG.
For example, as shown in FIG. 23A, the shape of the flow path cross section of the first cooling passage 61 and the second cooling passage 62 may be triangular. In this case, in the second cooling passage 62, it is preferable that one side 602 of the cross section of the flow path having a triangular shape when viewed along the axial direction Da faces the inside of the radial Dr of the main body 53. As a result, the distance between the second cooling passage 62 and the inner surface 531 can be reduced while increasing the projected area of the flow path cross section when viewed from the inner surface 531 of the main body 53 toward the outside in the radial direction. The cooling air CA flowing through the second cooling passage 62 can efficiently cool the area on the inner surface 531 side of the main body 53.
As shown in FIG. 23A, in the second cooling passage 62, when one side 602 of the flow path cross section having a triangular shape when viewed along the axial direction Da is directed toward the inside of the radial direction Dr of the main body 53. , One vertex 603 of the triangle points outward Dr in the radial direction. Therefore, as shown in FIG. 23A, in the first cooling passage 61, one apex 604 of a triangle having a triangular shape when viewed along the axial direction Da is directed to the inside of the radial Dr, and the apex is formed. If the 604 is overlapped with the second cooling passage 62 in the radial direction Dr, the thickness of the main body 53 along the radial direction Dr can be suppressed.

FIG. 23B is a diagram showing a part of still another embodiment of the FF arrow cross section of FIG.
For example, as shown in FIG. 23B, the shape of the flow path cross section of the first cooling passage 61 may be a rhombus, and the shape of the flow path cross section of the second cooling passage 62 may be a triangle. In this case, as in the example shown in FIG. 23A, in the second cooling passage 62, one side 602 of the flow path cross section having a triangular shape when viewed along the axial direction Da is inside the radial Dr of the main body 53. It is good to face it. As a result, the distance between the second cooling passage 62 and the inner surface 531 can be reduced while increasing the projected area of the flow path cross section when viewed from the inner surface 531 of the main body 53 toward the outside in the radial direction. The cooling air CA flowing through the second cooling passage 62 can efficiently cool the area on the inner surface 531 side of the main body 53.
As shown in FIG. 23B, in the second cooling passage 62, when one side 602 of the flow path cross section having a triangular shape when viewed along the axial direction Da is directed toward the inside of the radial direction Dr of the main body 53. , One vertex 603 of the triangle points outward Dr in the radial direction. Therefore, as shown in FIG. 23B, in the first cooling passage 61, one apex 605 of a rhombus having a rhombus shape when viewed along the axial direction Da is directed to the inside of the radial Dr, and the apex is formed. If the 605 is overlapped with the second cooling passage 62 in the radial direction Dr, the thickness of the main body 53 along the radial direction Dr can be suppressed.

The present disclosure is not limited to the above-described embodiment, and includes a modified form of the above-described embodiment and a combination of these embodiments as appropriate.

The contents described in each of the above embodiments are grasped as follows, for example.
(1) The high-temperature component according to at least one embodiment of the present disclosure has a plurality of first cooling passages 61 extending linearly and a plurality of first cooling passages 61 in a direction perpendicular to a plane including extending directions. A plurality of second cooling passages 62 extending along the extending direction of the first cooling passage 61 so as to be separated from the cooling passage 61 and communicate with any of the first cooling passages 61 are provided. The maximum value S1max of the cross-sectional area S1 of each first cooling passage 61 is from the maximum value S2max of the cross-sectional area S2 of the second cooling passage 62 closest to the first cooling passage 61 in the cross section orthogonal to the extending direction. Is also big.

As described above, in a machine operated by a high-temperature working gas such as a gas turbine 10, generally, the removal of heat by cooling leads to a decrease in the thermal efficiency of the machine. Therefore, it is desirable to efficiently cool high-temperature parts with as few cooling media as possible. Therefore, it is desirable to increase the flow rate of the cooling medium in the cooling passage 6 and improve the cooling capacity by reducing the flow path cross-sectional area S in the cooling passage 6.
However, as the flow path cross-sectional area S becomes smaller, the risk of the cooling passage 6 being blocked by foreign matter may increase.

According to the configuration of the above (1), since the plurality of first cooling passages 61 and the plurality of second cooling passages 62 separated from the first cooling passage 1 in the perpendicular direction are provided, the plurality of first cooling passages 61 are provided. Alternatively, the cooling capacity can be improved as compared with the case where only one of the plurality of second cooling passages 62 is provided. As a result, the cross-sectional area S of the cooling passage 6 can be increased while ensuring the cooling capacity as compared with the case where only one of the plurality of first cooling passages 61 or the plurality of second cooling passages 62 is provided. .. Therefore, as compared with the case where only one of the plurality of first cooling passages 61 or the plurality of second cooling passages 62 is provided, the risk of blockage in the cooling passage 6 can be suppressed while ensuring the cooling capacity.

Further, according to the configuration of the above (1), the maximum value S1max of the cross-sectional area S1 of each first cooling passage 61 is the second closest to the first cooling passage 61 in the cross section orthogonal to the extending direction. Compared with the case where the maximum value S2max of the cross-sectional area S2 of the cooling passage 62 is the same as or smaller than the maximum value S2max, the flow velocity of the cooling medium in the first cooling passage 61 can be suppressed and the static pressure can be increased. Therefore, when the flow direction of the cooling medium is the direction in which the cooling medium flows from the first cooling passage 61 toward the second cooling passage 62, the static in the first cooling passage 61 located on the upstream side of the second cooling passage 62. Since the pressure can be increased, the flow velocity of the cooling medium in the second cooling passage 62 can be increased, and the cooling capacity in the second cooling passage 62 can be improved.

(2) In some embodiments, in the configuration of (1) above, the maximum value S1max of the cross-sectional area S1 of each first cooling passage 61 is the second cooling passage 62 communicating with the first cooling passage 61. It is larger than the maximum value AS2max of the total cross-sectional area AS2.

According to the configuration of (2) above, the maximum value S1max of the cross-sectional area S1 of each first cooling passage 61 is the maximum value AS2max of the total cross-sectional area AS2 of the second cooling passage 62 communicating with the first cooling passage 61. Compared with the case where it is the same as or smaller than the above, the flow velocity of the cooling medium in the first cooling passage 61 can be suppressed and the static pressure can be increased. Therefore, when the flow direction of the cooling medium is the direction in which the cooling medium flows from the first cooling passage 61 toward the second cooling passage 62, the static in the first cooling passage 61 located on the upstream side of the second cooling passage 62. Since the pressure can be increased, the flow velocity of the cooling medium in the second cooling passage 62 can be increased, and the cooling capacity in the second cooling passage 62 can be improved.

(3) In some embodiments, in the configuration of (1) or (2), the maximum value H1max of the dimension H1 of each first cooling passage 61 in the perpendicular direction communicates with the first cooling passage 61. It is larger than the maximum value H2max of the dimension H2 in the vertical direction of the second cooling passage 62.

According to the configuration of the above (3), the maximum value H1max of the dimension H1 of each first cooling passage 61 in the perpendicular direction is the dimension H2 of the second cooling passage 62 communicating with the first cooling passage 61 in the perpendicular direction. By making it larger than the maximum value H2max of, the maximum value S1max of the cross-sectional area S1 of each first cooling passage 61 is set to the second cooling closest to the first cooling passage 61 in the cross section orthogonal to the extending direction. It can be made larger than the maximum value S2max of the cross-sectional area S2 of the passage 62.

(4) In some embodiments, in any of the configurations (1) to (3), the dimension W1 of each first cooling passage 61 in the passage width direction orthogonal to the perpendicular direction and the extension direction. The maximum value W1max of is larger than the maximum value W2max of the dimension W2 in the passage width direction of the second cooling passage 62 communicating with the first cooling passage 61.

According to the configuration of (4) above, the maximum value W1max of the dimension W1 of each first cooling passage 61 in the passage width direction is the dimension in the passage width direction of the second cooling passage 62 communicating with the first cooling passage 61. By making it larger than the maximum value W2max of W2, the maximum value S1max of the cross-sectional area S1 of each first cooling passage 61 is set to the second closest to the first cooling passage 61 in the cross section orthogonal to the extending direction. It can be made larger than the maximum value S2max of the cross-sectional area S2 of the cooling passage 62.

(5) In some embodiments, in any of the configurations (1) to (4) above, each first cooling passage 61 is connected to a second cooling passage 62 communicating with the first cooling passage 61. The connection end portion (upstream side connection end portion) 61a to be formed is included. In each first cooling passage 61, the cross-sectional area S1 in the region on the upstream side connection end 61a side is larger than the cross-sectional area S1 in the region farther from the upstream connection end 61a than the region.

According to the configuration of (5) above, in each of the first cooling passages 61, the cross-sectional area S1 is larger in the region closer to the second cooling passage 62. Therefore, when the flow direction of the cooling medium is the direction in which the cooling medium flows from the first cooling passage 61 toward the second cooling passage 62, the first cooling passage 61 located on the upstream side of the second cooling passage 62. Since the static pressure in the region closer to the second cooling passage 62 can be improved, the flow velocity of the cooling medium in the second cooling passage 62 can be efficiently increased, and the cooling capacity in the second cooling passage 62 can be efficiently improved.

(6) In some embodiments, in any of the configurations (1) to (5), the high temperature component according to at least one embodiment of the present disclosure is a passage orthogonal to the perpendicular direction and the extending direction. A first partition wall 71 for partitioning the first cooling passages 61 adjacent to each other along the width direction and a second partition wall 72 for partitioning the second cooling passages 62 adjacent to each other along the width direction are further provided. When viewed from the vertical direction, the first partition wall 71 is arranged at substantially the same position as the second partition wall 72 in the passage width direction.

According to the configuration of (6) above, when viewed from the vertical direction, the first partition wall 71 and the second partition wall 72 are arranged at substantially the same position in the passage width direction. The structure of the connecting portion between the cooling passage 61 and the second cooling passage 62 can be simplified.

(7) In some embodiments, in any of the configurations (1) to (5), the high temperature component according to at least one embodiment of the present disclosure is a passage orthogonal to the perpendicular direction and the extending direction. A first partition wall 71 for partitioning the first cooling passages 61 adjacent to each other along the width direction and a second partition wall 72 for partitioning the second cooling passages 62 adjacent to each other along the width direction are further provided. When viewed from the vertical direction, the first partition wall 71 is arranged at a position substantially different from that of the second partition wall 72 in the passage width direction.

According to the configuration (7), when viewed from the vertical direction, the first partition wall 71 and the second partition wall 72 are arranged at substantially the same position in the passage width direction. When viewed from the vertical direction, the area where the first partition wall 71 and the second cooling passage 62 overlap increases, and the area where the second partition wall 72 and the first cooling passage 61 overlap increases. As a result, for example, the heat transmitted between the two adjacent first cooling passages 61 through the first partition wall 71 is easily transferred to the cooling medium flowing through the second cooling passage 62. Further, for example, the heat transmitted between the two adjacent second cooling passages 62 through the second partition wall 72 is easily transferred to the cooling medium flowing through the first cooling passage 61.

(8) In some embodiments, in any of the configurations (1) to (7) above, the high temperature component according to at least one embodiment of the present disclosure includes each first cooling passage 61 and the first cooling. A plurality of first folded passages 66, which are connected to each other with the second cooling passage 62 communicating with the passage 61, are further provided.

According to the configuration of (8) above, each of the first cooling passages 61 and the second cooling passage 62 communicating with the first cooling passage 61 can be connected by the first folded passage 66.

(9) In some embodiments, in the configuration of (8) above, the high temperature component according to at least one embodiment of the present disclosure has an opening 515 facing a plurality of first folding passages 66 and an opening 515. A closing member 517 for closing is further provided.

According to the configuration of (9) above, the first cooling passage 61 and the second cooling passage 62 can be accessed from the opening 515 through the first folding passage 66. Thereby, for example, it can be confirmed whether or not the first cooling passage 61 and the second cooling passage 62 have a specified opening area at the manufacturing stage of the high temperature parts, which contributes to the quality control of the high temperature parts.

(10) In some embodiments, in the configuration of (8) or (9), the high temperature component according to at least one embodiment of the present disclosure is in the passage width direction orthogonal to the perpendicular direction and the extension direction. A folding passage partition wall 76, which separates the first folding passages 66 adjacent to each other along the same, is further provided.

According to the configuration of (10) above, the first turn-back passages 66 adjacent to each other can be separated from each other along the passage width direction. Further, according to the configuration of (10) above, the folding passage partition wall 76 functions as a heat transfer member to the cooling medium flowing through the first folding passage 66, so that the cooling capacity can be improved.

(11) In some embodiments, in the configuration of (10) above, the high temperature component according to at least one embodiment of the present disclosure has an opening 515 facing a plurality of first folding passages 66 and an opening 515. A closing member 517 for closing is further provided. The closing member 517 is in contact with at least a part of the folded passage partition wall 76.

According to the configuration of (11) above, the first cooling passage 61 and the second cooling passage 62 can be accessed from the opening 515 through the first folding passage 66. Thereby, for example, it can be confirmed whether or not the first cooling passage 61 and the second cooling passage 62 have a specified opening area at the manufacturing stage of the high temperature parts, which contributes to the quality control of the high temperature parts.
Further, according to the configuration (11), the closing member 517 comes into contact with at least a part of the folded passage partition wall 76, so that the closing member 517 can be easily positioned at the opening 515.

(12) In some embodiments, in any of the configurations (8) to (11), at least a part of the plurality of first folding passages 66 is one end face in the extending direction of the high temperature component. It exists at a distance within twice the passage height H6 of the first turn-back passage 66 in the vertical direction from (upstream end surface 513a).

In the first folded passage 66, since the first cooling passage 61 and the second cooling passage 62 having different positions in the vertical line direction are connected, the direction of the flow of the cooling medium changes, so that the cooling medium in the first folded passage 66 is connected. The heat transfer coefficient to is improved. Therefore, the cooling capacity of the region near the first folding passage 66 in the high temperature component is improved.
For example, when the heat load is higher in the vicinity of the end face on one side in the extending direction of the high temperature component than in the other region, it is desirable to arrange the first folding passage 66 in the vicinity of the end face. Therefore, according to the configuration (12), the high-temperature component can be efficiently cooled in the vicinity of the end face on one side in the extending direction of the high-temperature component when the heat load is higher than that of the other region.

(13) In some embodiments, in any of the configurations (8) to (12), the high temperature component according to at least one embodiment of the present disclosure includes a plurality of second cooling passages 62 in the vertical direction. Is separated from the first cooling passage 61 on the opposite side and extends along the extending direction of the first cooling passage 61 so as to communicate with any of the first cooling passages 61, and a plurality of first cooling passages 64. A second folding passage 65 that connects the cooling passage 61 and the introduction passage 64 to each other is further provided.

In the second folding passage 65, since the introduction passage 64 and the first cooling passage 61 having different positions in the vertical line direction are connected, the direction of the flow of the cooling medium changes, so that the cooling medium in the second folding passage 65 can be connected to the cooling medium. The heat transfer coefficient is improved. Therefore, according to the configuration of (13) above, the cooling capacity of the region near the second folding passage 65 in the high temperature component is improved.

(14) In some embodiments, in the configuration of (13) above, at least a portion of the plurality of first folding passages 66 is present on one side of the high temperature component in the extending direction. At least a part of the second folded passage 65 exists at a distance within three times the passage height H5 of the second folded passage 65 in the vertical direction from the other end surface in the extending direction in the high temperature component.

As described above, since the heat transfer coefficient to the cooling medium in the second folded passage 65 is improved, the cooling capacity of the region near the second folded passage 65 in the high temperature component is improved.
For example, when the heat load is higher than the other regions in the vicinity of the end face on the other side in the extending direction of the high temperature component, it is desirable to arrange the second folding passage 65 in the vicinity of the end face. Therefore, according to the configuration (14), the high-temperature component can be efficiently cooled in the vicinity of the end face on the other side in the extending direction of the high-temperature component when the heat load is higher than that of the other regions.

(15) In some embodiments, in any of the configurations (1) to (14) above, the high temperature component comprises a split ring 50 of the gas turbine 10 formed annularly along the circumferential direction. Body 51.

According to the configuration of (15) above, the split body 51 includes any of the configurations (1) to (14) above, so that the cooling capacity of the split body 51 is secured and the cross-sectional area S of the cooling passage 6 S. Can be increased, so that the risk of blockage in the cooling passage 6 can be suppressed.
Further, according to the configuration of (15) above, the flow velocity of the cooling medium in the second cooling passage 62 can be increased, and the cooling capacity in the second cooling passage 62 can be improved, so that the second cooling passage is more than the first cooling passage 61. By arranging the second cooling passage 62 so that the 62 is closer to the surface exposed to the high temperature gas, the divided body 51 can be effectively cooled.

(16) In some embodiments, in any of the configurations (1) to (15) above, the high temperature component (divided body 51) is a three-dimensional laminated model.

According to the configuration (16) above, even a high-temperature component provided with an elongated cooling passage that is difficult to process by electric discharge machining can be obtained as a three-dimensional laminated model.

(17) The rotary machine (gas turbine 10) according to at least one embodiment of the present disclosure includes high-temperature parts having any of the above configurations (1) to (16).

According to the configuration (17) above, the risk of blockage of the cooling passage in the high temperature component of the rotating machine can be suppressed, and the reliability of the rotating machine can be improved.

6 Cooling passage 10 Gas turbine 50 Divided ring 51 Divided body 53 Main body 55 Protruding part 57 Connection part 59 Hook 61 1st cooling passage 62 2nd cooling passage 64 Introduction passage 65 2nd turn-back passage (entrance side turn-back passage)
66 First turnaround passage (intermediate turnaround passage)
71 1st partition wall 72 2nd partition wall 515 Opening 517 Closing member 531 Inner surface 532 Outer surface

Claims (17)

A plurality of first cooling passages extending in a straight line and
The extending direction of the first cooling passage so as to be separated from the first cooling passage in the perpendicular direction of the plane including the extending direction of the plurality of first cooling passages and communicate with any of the first cooling passages. With multiple second cooling passages extending along
With
The maximum value of the cross-sectional area of each of the first cooling passages is larger than the maximum value of the cross-sectional area of the second cooling passage closest to the first cooling passage in the cross section orthogonal to the extending direction. The high-temperature component according to claim 1, wherein the maximum value of the cross-sectional area of each of the first cooling passages is larger than the maximum value of the total cross-sectional area of the second cooling passage communicating with the first cooling passage. The maximum value of the dimension of each of the first cooling passages in the perpendicular direction is larger than the maximum value of the dimension of the second cooling passage communicating with the first cooling passage in the perpendicular direction according to claim 1 or 2. High temperature parts. The maximum value of the dimension of each of the first cooling passages in the passage width direction orthogonal to the vertical direction and the extending direction is the dimension in the passage width direction of the second cooling passage communicating with the first cooling passage. The high temperature component according to any one of claims 1 to 3, which is larger than the maximum value. Each said first cooling passage includes a connecting end connected to the second cooling passage communicating with the first cooling passage.
The first cooling passage according to any one of claims 1 to 4, wherein the cross-sectional area in the region on the connection end side is larger than the cross-sectional area in the region farther from the connection end than the region. High temperature parts. A first partition wall that separates the first cooling passages that are adjacent to each other along the passage width direction that is orthogonal to the vertical direction and the extension direction.
A second partition wall that separates the second cooling passages that are adjacent to each other along the passage width direction,
With more
The invention according to any one of claims 1 to 5, wherein the first partition wall is arranged at substantially the same position as the second partition wall in the passage width direction when viewed from the vertical direction. High temperature parts. A first partition wall that separates the first cooling passages that are adjacent to each other along the passage width direction that is orthogonal to the vertical direction and the extension direction.
A second partition wall that separates the second cooling passages that are adjacent to each other along the passage width direction,
With more
The invention according to any one of claims 1 to 5, wherein the first partition wall is arranged at a substantially different position in the passage width direction from the second partition wall when viewed from the vertical direction. High temperature parts. The high temperature according to any one of claims 1 to 7, further comprising a plurality of first folded passages connecting each of the first cooling passages and the second cooling passages communicating with the first cooling passages to each other. parts. With the openings facing the plurality of first turn-back passages,
A closing member that closes the opening,
8. The high temperature component according to claim 8. The high-temperature component according to claim 8 or 9, further comprising a folded passage partition wall that separates the first folded passages that are adjacent to each other along the passage width direction orthogonal to the perpendicular direction and the extending direction. With the openings facing the plurality of first turn-back passages,
A closing member that closes the opening,
With more
The high-temperature component according to claim 10, wherein the closing member is in contact with at least a part of the folded passage partition wall. At least a part of the plurality of first folded passages exists at a distance within twice the height of the passage of the first folded passage in the perpendicular direction from one end surface of the high temperature component in the extending direction. The high temperature component according to any one of claims 8 to 11. Along the extending direction of the first cooling passage so as to be separated from the first cooling passage on the side opposite to the plurality of second cooling passages in the perpendicular direction and communicate with any of the first cooling passages. Introductory passages that extend
A second folding passage connecting the plurality of first cooling passages and the introduction passage to each other,
The high temperature component according to any one of claims 8 to 12, further comprising. At least a part of the plurality of first turn-back passages exists on one side in the extending direction in the high temperature component.
Claim that at least a part of the second folding passage exists at a distance within three times the height of the passage of the second folding passage in the perpendicular direction from the other end surface in the extending direction in the high temperature component. 13. The high temperature component according to 13. The high-temperature component according to any one of claims 1 to 14, wherein the high-temperature component is a split body forming a split ring of a gas turbine formed in an annular shape along the circumferential direction. The high-temperature component according to any one of claims 1 to 15, wherein the high-temperature component is a three-dimensional laminated model. A rotary machine including the high temperature component according to any one of claims 1 to 16.

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