HIGH-TEMPERATURE COMPONENT AND MANUFACTURING PROCESS FOR HIGH-TEMPERATURE COMPONENT

Abstract

A high-temperature component used for a turbomachine that must be cooled by a cooling medium, having the following characteristics: a multitude of cooling channels (60) through which the cooling medium can flow; a headpiece (80) which is connected to the respective downstream ends (65) of the plurality of cooling channels (60); and one or more outlet channels (110) for expelling the cooling medium flowing into the headpiece (80) to the outside of the headpiece (80), wherein the one or more outlet channels (110) are present in fewer numbers than the multitude of cooling channels (60), wherein the respective minimum flow channel cross-sectional areas (SBmin) of the one or more outlet channels (110) are not smaller than the respective flow channel cross-sectional areas (SA) of the plurality of cooling channels (60) in a connection between the headpiece (80) and the cooling channels (60), wherein a sum of the respective minimum flow channel cross-sectional areas (SBmin) of the one or more outlet channels (110) is smaller than a sum of the respective flow channel cross-sectional areas (SA) of the plurality of cooling channels (60) in the connection between the headpiece (80) and the cooling channels (60), wherein the one or more outlet channels (110) each have an inner wall surface (110c) whose mean-line average roughness Ra is not greater than 10 µm in a region (115) where the flow channel cross-sectional area of ​​the outlet channel (110) is minimal, and wherein the plurality of cooling channels (60) each has an inner wall surface (60a) whose mean line average roughness Ra is not less than 10 µm and not greater than 20 µm.

Description

TECHNICAL AREA

[0001] The present invention relates to a high-temperature component and a manufacturing process for the high-temperature component. BACKGROUND

[0002] For example, components in a machine, such as a gas turbine, through which a high-temperature working gas flows, comprise a high-temperature component that must be cooled by a cooling medium. A cooling structure of the high-temperature component is known as a structure in which the high-temperature component is cooled by causing cooling air to flow through a plurality of transport channels (cooling channels) that allow the cooling air to flow within the component (see patent specification 1).

[0003] Patent specification 2 discloses a gas turbine with a turbine rotor rotatably mounted on a shaft in a housing, wherein the turbine rotor extends substantially perpendicular to the axis of the shaft and has turbine blades attached to its outer edge with intermediate platform devices, the blades receive a driving force from a hot working fluid moving in a direction generally parallel to the axis of the shaft, and the driving force is transmitted to the shaft via the turbine rotor, and furthermore, devices arranged radially inside the platform are provided for introducing a liquid coolant into the turbine in a radially outward direction into an open coolant distribution system, which has cooling channels located below the surface that run approximately radially in each blade.The platforms include devices for metering the fluid in fluid communication with the cooling channels, and a distributor and outlet section is provided at the end of each rotor blade in fluid communication with the outer ends of the cooling channels of a rotor blade, whereby the coolant flows to the underside of the platform devices, is metered there into the cooling channels, passes through them, and exits from these cooling channels into the distributor and outlet section of the open coolant distribution system. The gas turbine comprises distributor devices on the rotor blade surface near the end of each rotor blade in fluid communication with the outlet end of each cooling channel, and a convergent-divergent nozzle in fluid communication with the distributor devices for discharged the coolant flow from the open-circuit coolant distribution system.

[0004] Patent specification 3 discloses that a ring segment for a gas turbine engine comprises a plate and a cooling system. The cooling system receives cooling fluid from an outer surface of the plate to cool the plate and comprises at least one cooling fluid supply channel, at least one serpentine cooling channel, and at least one cooling fluid outlet channel. The cooling fluid supply channel(s) receives the cooling fluid from the outer surface of the plate and directs the cooling fluid to a first cooling fluid chamber within the plate. The serpentine cooling channel(s) receives the cooling fluid from the first cooling fluid chamber, the cooling fluid convectively cooling the plate as it flows through the serpentine cooling channel(s). The cooling fluid outlet channel(s) discharges the cooling fluid from the cooling system.

[0005] Patent specification 4 discloses that a gas turbine combustion chamber comprises: an inlet manifold provided on a combustion gas outlet side of a wall section of an inner tube, which is tubular in shape so that a combustion gas stream forms therein; a plurality of cooling channels connected to the inlet manifold and arranged in the wall section parallel to the flow direction of the combustion gas; and a cooling air outlet section connected to the cooling channels and located on an exhaust gas upstream side of the wall section. The gas turbine combustion chamber is characterized in that the cross-sectional area of ​​the cooling channels is reduced in the direction of the cooling air flow. Citation list for patent literature Patent specification 1: JP 2015-48848 A Patent specification 2: DE 23 43 639 A Patent specification 3: US 2012 / 0057968 A1 Patent specification 4: JP 2008-274774 A SUMMARY Technical Problem

[0006] In a machine, such as a gas turbine, which is driven by a high-temperature working gas, heat loss through cooling generally leads to a reduction in the machine's thermal efficiency. Therefore, it is desirable to cool a temperature-sensitive component efficiently with as little cooling medium as possible. For this reason, it is preferable that the cross-sectional area of ​​the flow channel in a cooling duct should not be larger than necessary.

[0007] However, if the cross-sectional area of ​​the flow channel is small, the dimensional accuracy of the cooling channel tends to decrease due to a manufacturing limitation of the high-temperature component, which can reduce the accuracy of the flow rate of cooling air in the cooling channel.

[0008] If the accuracy of the cooling air flow rate in the cooling duct is reduced, and the cooling air flow rate is higher than a set rate, more heat will be extracted by the cooling air than necessary, which can reduce the thermal efficiency of the machine. Furthermore, if the cooling air flow rate is lower than the set rate, the high-temperature component can be damaged by faulty cooling.

[0009] In view of the foregoing, an object of at least one embodiment of the present invention is to provide the high-temperature component which is able to avoid a deficiency in cooling capacity while suppressing excessive cooling. Solution to the problem

[0010] The present invention provides a high-temperature component according to independent claims 1, 2 and 7, and a manufacturing method for a high-temperature component according to independent claim 8. Advantageous modifications are found in the dependent claims.

[0011] (1) A high-temperature component according to at least one embodiment of the present invention is a high-temperature component used for a turbomachine and which requires cooling by a cooling medium, the component comprising: a plurality of cooling channels through which the cooling medium can flow; a headpiece connected to the respective downstream ends of the plurality of cooling channels; and one or more outlet channels for expelling the cooling medium flowing into the headpiece to the outside of the headpiece. The one or more outlet channels are fewer in number than the plurality of cooling channels. The respective minimum cross-sectional areas of the flow channels of the one or more outlet channels are not smaller than the respective cross-sectional areas of the flow channels of the plurality of cooling channels in a connection between the headpiece and the cooling channels.The sum of the respective minimum flow channel cross-sectional areas of one or more outlet channels is smaller than the sum of the respective flow channel cross-sectional areas of the multitude of cooling channels in the connection between the headpiece and the cooling channels.

[0012] In the event that the flow rate of the cooling medium flowing through each of the plurality of cooling channels is determined by each of the flow channel cross-sectional areas of the plurality of cooling channels, if the flow channel cross-sectional area is small, the dimensional accuracy of the cooling channels tends to decrease due to a manufacturing limitation of the high-temperature component as described above, which can reduce the accuracy of the flow rate of the cooling medium in the cooling channels.

[0013] In contrast, with the above configuration (1), it is possible to define the flow rate of the cooling medium in the plurality of cooling channels by the minimum cross-sectional areas of the cooling channels, since the sum of the respective minimum cross-sectional areas of the one or more outlet channels is smaller than the sum of the respective cross-sectional areas of the cooling channels in the connection between the headpiece and the cooling channels. Thus, in each of the plurality of cooling channels, the cross-sectional area does not need to be reduced more than necessary to control the flow rate of the cooling medium, thereby improving the dimensional accuracy of the cooling channels and suppressing changes in the flow rate of the cooling medium among the plurality of cooling channels. Therefore, it is possible to avoid a lack of cooling capacity while suppressing excessive cooling.

[0014] Furthermore, since with the above configuration (1) the respective minimum flow channel cross-sectional areas of the one or more outlet channels are not smaller than the respective flow channel cross-sectional areas of the plurality of cooling channels in the connection between the headpiece and the cooling channels, dimensional accuracy of the outlet channel is easily ensured, and blockage in the outlet channel by a foreign substance hardly occurs.

[0015] Furthermore, since with the above configuration (1) the one or more outlet channels are present in smaller numbers than the multitude of cooling channels, it is possible with regard to the management of the flow rate of the cooling medium to reduce a section in which accuracy of the flow channel cross-sectional area, i.e. the dimensional accuracy of the channel, is to be ensured and manufacturing costs of the high temperature component are to be suppressed.

[0016] (2) In some embodiments of the above configuration (1), a separation distance between an upstream inner wall and a downstream inner wall of the headpiece is at least once and at most three times greater than an equivalent diameter of a region in which the flow channel cross-sectional area of ​​the outlet channel is minimal.

[0017] If the upstream inner wall, i.e., connection positions between the headpiece and the respective downstream ends of the plurality of cooling channels, and the downstream inner wall, i.e., connection positions between the headpiece and the respective upstream ends of the one or more outlet channels, are too close together, the difference in the flow rate of the cooling medium increases between the cooling channel whose distance between the downstream end of the cooling channel and the upstream end of the outlet channel is small, and the cooling channel whose distance between the downstream end and the upstream end is large.

[0018] In contrast, with the above configuration (2) it is possible to suppress the change in the flow rate of the cooling medium under the plurality of cooling channels, since the upstream inner wall, i.e. the connection positions between the headpiece and the respective downstream ends of the plurality of cooling channels, and the downstream inner wall, i.e. the connection positions between the headpiece and the respective upstream ends of the one or more outlet channels, are separated from each other by a distance that is at least once greater than the equivalent diameter described above.

[0019] Furthermore, since the respective downstream ends of the multitude of cooling channels are connected to the headpiece, the volume within the headpiece increases, and the flow velocity of the cooling medium within the headpiece decreases, thereby reducing the heat transfer coefficient to the cooling medium. Consequently, the cooling capacity within the headpiece can be reduced, and thus it is preferable that the separation distance between the upstream and downstream inner walls be small.

[0020] In this respect, the above configuration (2) makes it possible to suppress the occurrence of a region where the cooling capacity in the high-temperature component is faulty, since the separation distance between the upstream inner wall and the downstream inner wall is at most three times greater than the equivalent diameter described above.

[0021] (3) In some embodiments, the one or more outlet channels in the above configuration (1) or (2) each comprise a reduced section of the flow channel cross-sectional area in which the flow channel cross-sectional area of ​​the outlet channel is gradually reduced in the direction of a downstream side.

[0022] With the above configuration (3), a dimension is set in a direction orthogonal to the extension direction of the outlet channel from a downstream side of the reduced section of the flow channel cross-sectional area, thereby easily adjusting the minimum flow channel cross-sectional area of ​​the outlet channel. Therefore, it is possible to manage the flow rate of the cooling medium as long as the dimension in the direction orthogonal to the extension direction of the outlet channel downstream of the outlet channel is managed. This makes it possible to limit the area in which accuracy of the flow channel cross-sectional area, i.e., dimensional accuracy of the channel, is required, and to suppress the manufacturing costs of the high-temperature component.

[0023] (4) In some embodiments according to one of the above configurations (1) to (3), the one or more outlet channels each have an inner wall surface whose mean-line average roughness Ra is not greater than 10 µm in a region where the flow channel cross-sectional area of ​​the outlet channel is minimal, and the plurality of cooling channels each have an inner wall surface whose mean-line average roughness Ra is not less than 10 µm and not greater than 20 µm.

[0024] With the above configuration (4), it is possible to improve the cooling performance in the cooling channels, since the respective inner wall surfaces of the multitude of cooling channels exhibit the roughness described above. Furthermore, with the above configuration (4), it is possible to suppress changes in pressure loss in the outlet channel and to facilitate the passage of foreign matter through the outlet channel, since an inner wall surface of the outlet channel in the area where the flow channel cross-sectional area of ​​the outlet channel is minimal exhibits the roughness described above, thereby reducing the risk of clogging of the outlet channel.

[0025] (5) In some embodiments according to one of the above configurations (1) to (4), walls forming the plurality of cooling channels have chamfered corners at downstream ends of the cooling channels.

[0026] The walls forming the multiple cooling channels can each have the thinnest possible wall thickness, as required to improve heat transfer performance. If, in this case, the corner has a shape that is not chamfered at the downstream end of the cooling channel, the corner's shape may be lost when the high-temperature component is formed, for example, by precision casting or additive manufacturing of a metal, and if subsequent heat treatment is performed. If the corner's shape is lost, it negatively affects the flow of the cooling medium through the cooling channel, potentially reducing cooling performance.

[0027] In contrast, with the above configuration (5) it is possible to suppress the negative effect caused by the loss of shape of the corner described above.

[0028] (6) In some embodiments according to one of the above configurations (1) to (5), the number of outlet channels is one.

[0029] As described above, with regard to managing the flow rate of the cooling medium, it is desirable to reduce the section where accuracy of the flow channel cross-sectional area, i.e., dimensional accuracy of the channel, is required. In this respect, with the configuration (6) described above, it is possible to reduce the section where dimensional accuracy of the channel is required and to suppress the manufacturing costs of the high-temperature component, since the number of outlet channels is one.

[0030] (7) In some embodiments according to one of the preceding configurations (1) to (6), the high-temperature component represents ring segments of a gas turbine, each consisting of a plurality of segment bodies formed in a ring shape along a circumferential direction, each plurality of segment bodies having an inner surface facing a fuel gas flow path through which a fuel gas flows, each plurality of cooling channels being formed in each plurality of segment bodies, and each of the one or more outlet channels being open in an axial direction into the fuel gas at each downstream end of the plurality of segment bodies.

[0031] With the above configuration (7), the sum of the respective minimum cross-sectional areas of the flow channels of the one or more outlet channels is smaller than the sum of the respective cross-sectional areas of the flow channels of the plurality of cooling channels in the connection between the head and the cooling channels, since the ring segments of the gas turbine have one of the above configurations (1) to (6). Thus, it is possible to define the flow rate of the cooling medium in the plurality of cooling channels by the minimum cross-sectional areas of the cooling channels. Therefore, in each of the plurality of cooling channels, the cross-sectional area of ​​the flow channel does not need to be reduced more than necessary to control the flow rate of the cooling medium, thereby improving the dimensional accuracy of the cooling channels and making it possible to suppress changes in the flow rate of the cooling medium among the plurality of cooling channels.Therefore, it is possible to avoid a deficiency in cooling capacity while suppressing excessive cooling in the ring segments.

[0032] Furthermore, with the above configuration (7) dimensional accuracy of the outlet channel in the ring segments is easily ensured and blockage in the outlet channel by a foreign substance hardly occurs, since the respective minimum flow channel cross-sectional areas of the one or more outlet channels are not smaller than the respective flow channel cross-sectional areas of the multitude of cooling channels in the connection between the head piece and the cooling channels.

[0033] Furthermore, with the above configuration (7) it is possible to reduce the section in which accuracy of the flow channel cross-sectional area, i.e. dimensional accuracy of the channel, is to be ensured, and to suppress manufacturing costs of the ring segments, since the one or more outlet channels are present in fewer numbers than the multitude of cooling channels with regard to managing the flow rate of the cooling medium.

[0034] (8) A manufacturing method for a high-temperature component according to at least one embodiment of the present invention is a manufacturing method for a high-temperature component used for a turbomachine and which requires cooling by a cooling medium, comprising: a step for forming a plurality of cooling channels through which the cooling medium can flow; a step for forming a headpiece connected to the respective downstream ends of the plurality of cooling channels; and a step for forming one or more outlet channels for expelling the cooling medium flowing into the headpiece to the outside of the headpiece. The one or more outlet channels are present in fewer numbers than the plurality of cooling channels.The respective minimum cross-sectional areas of the flow channels of one or more outlet channels are not smaller than the respective cross-sectional areas of the multiple cooling channels in a connection between the headpiece and the cooling channels. The sum of the respective minimum cross-sectional areas of the flow channels of one or more outlet channels is smaller than the sum of the respective cross-sectional areas of the multiple cooling channels in the connection between the headpiece and the cooling channels.

[0035] The preceding method (8) makes it possible to define the flow rate of the cooling medium in the plurality of cooling channels by the minimum cross-sectional areas of the cooling channels, since the sum of the respective minimum cross-sectional areas of the one or more outlet channels is smaller than the sum of the respective cross-sectional areas of the cooling channels in the connection between the headpiece and the cooling channels. Thus, in each of the plurality of cooling channels, the cross-sectional area need not be reduced more than necessary to control the flow rate of the cooling medium, thereby improving the dimensional accuracy of the cooling channels and suppressing changes in the flow rate of the cooling medium among the plurality of cooling channels. Therefore, it is possible to avoid a deficiency in cooling capacity while suppressing excessive cooling.

[0036] Furthermore, the above method (8) easily ensures the dimensional accuracy of the outlet channel, and blockage in the outlet channel by a foreign substance hardly occurs, since the respective minimum flow channel cross-sectional areas of the one or more outlet channels cannot be smaller than the respective flow channel cross-sectional areas of the multitude of cooling channels in the connection between the headpiece and the cooling channels.

[0037] Furthermore, the above method (8) makes it possible to reduce the section in which the accuracy of the flow channel cross-sectional area, i.e. the dimensional accuracy of the channel, is to be ensured, and to suppress manufacturing costs of the high-temperature component, since the one or more outlet channels represent a smaller number than the multitude of cooling channels with respect to managing the flow rate of the cooling medium.

[0038] (9) In some embodiments according to the preceding method (8), the step of forming the one or more outlet channels comprises forming the one or more outlet channels such that each comprises a reduced section of a flow channel cross-sectional area in which the flow channel cross-sectional area of ​​the outlet channel is gradually reduced in the direction of a downstream side.

[0039] With the above method (9), it is only necessary to manage the dimensional accuracy of the most downstream region in the reduced section of a flow channel cross-sectional area, since the outlet channel is designed such that the reduced section of the flow channel cross-sectional area has the minimum flow channel cross-sectional area in the outlet channel with respect to managing the flow rate of the cooling medium. Thus, it is possible to limit the area in which the accuracy of the flow channel cross-sectional area, i.e., the dimensional accuracy of the channel, is to be ensured, and to suppress the manufacturing costs of the high-temperature component.

[0040] (10) In some embodiments according to the preceding method (8) or (9), the step of forming the one or more outlet channels comprises forming the one or more outlet channels by a method for the additive manufacturing of a metal or a precision casting process, and the method further comprises a step of performing a machining of at least a part of an inner wall surface of each of the one or more outlet channels.

[0041] The above method (10) makes it possible to reduce the manufacturing costs of the high-temperature component compared to forming the outlet channel by machining alone. Furthermore, the above method (10) makes it possible to improve the dimensional accuracy of the inner wall surface of the outlet channel and to improve the control accuracy of the coolant flow rate compared to forming the outlet channel by additive manufacturing of a metal or precision casting alone. Additionally, the above method (10) makes it possible to adjust the dimensions of the inner wall surface of the outlet channel while monitoring the coolant flow rate, thus enabling the correction of excess or deficiency in the coolant flow rate.

[0042] (11) In some embodiments of the preceding method (10), the step of performing a machining operation includes cutting one or more outlet channels with a drill.

[0043] Since it is possible to define the dimension of the inner wall surface of the outlet channel by the diameter of the drill using the above method (11), the high-temperature component is easily manufactured. Beneficial effects

[0044] According to at least one embodiment of the present invention, it is possible to provide a high-temperature component that is able to avoid a lack of cooling capacity while suppressing excessive cooling. BRIEF DESCRIPTION OF THE DRAWINGS Fig. Figure 1 is a schematic view showing the overall configuration of a gas turbine. Fig. Figure 2 is a cross-sectional view showing a gas flow path of a turbine. Fig. Figure 3 shows a schematic top view of a segment body viewed from an outside in the radial direction, and a schematic side view of the segment body viewed from a downstream side in a rotation direction of the rotor towards an upstream side in the rotation direction along the circumferential direction according to some embodiments. Fig. 4 is a cross-sectional view along the line A4-A4 in Fig. 3. Fig. Figure 5 is an enlarged view of the area surrounding a headpiece in Fig. 4. Fig. Figure 6 is a flowchart showing an example of a production procedure for the case where the segment body is produced by an additive manufacturing process of a metal according to some embodiments. Fig. Figure 7 is a view describing an exhaust port cutting step. DETAILED DESCRIPTION

[0045] Some embodiments of the present invention are described below with reference to the accompanying drawings. However, it is intended that dimensions, materials, shapes, relative positions, and the like of components described or shown in the drawings as embodiments are to be understood as illustrative only and do not serve to limit the scope of the present invention, unless they are specifically identified.

[0046] For example, an expression for a relative or absolute arrangement such as "in a direction", "along a direction", "parallel", "orthogonal", "centered", "concentric" and "coaxial" is not to be interpreted as only denoting the arrangement in a strictly literal sense, but also encompassing a state in which the arrangement is shifted relative by a tolerance or by an angle or a distance, making it possible to achieve the same function.

[0047] For example, an expression for an identical state such as "the same", "equal" and "uniform" is not to be interpreted as only denoting the state in which the feature is strictly identical, but also encompassing a state in which there is a tolerance or a difference through which the same function can nevertheless be achieved.

[0048] Furthermore, for example, an expression of a shape such as a rectangular shape or a tubular shape is not only to be interpreted as the geometrically strict shape, but also includes a shape with irregularities or chamfered corners within the area in which the same effect can be achieved.

[0049] On the other hand, the terms “possessing”, “comprising”, “with”, “containing” and “constituting” are not exclusive terms for one component that exclude the presence of other components.

[0050] A high-temperature component according to some embodiments is described below, taking into account a high-temperature component used for a gas turbine as an example.

[0051] Fig. Figure 1 is a schematic view showing the overall configuration of the gas turbine. Fig. Figure 2 is a cross-sectional view showing a gas flow path of a turbine.

[0052] In the present embodiment, a gas turbine 10 is configured as shown in Fig. Figure 1 shows that a compressor 11, a combustion chamber 12, and a turbine 13 are arranged coaxially by a rotor 14, and the rotor 14 is coupled at one end to a generator 15. In the following description, a direction in which the axis of the rotor 14 extends is referred to as an axial direction Da, a circumferential direction centered on the axis of the rotor 14 is referred to as a circumferential direction Dc, and a direction perpendicular to an axis Ax of the rotor 14 is referred to as a radial direction Dr. Furthermore, a rotational direction of the rotor 14 from the circumferential direction Dc is referred to as a rotational direction R.

[0053] Compressor 11 generates high-temperature / high-pressure compressed air AC by causing air AI drawn from an air inlet to pass through a multitude of guide vanes and rotor blades for compression. Compressor 11 generates high-temperature / high-pressure fuel gas FG by adding a predetermined fuel FL to the compressed air AC for combustion. Turbine 13 rotates the rotor 14 by causing the high-temperature / high-pressure fuel gas FG generated by the combustion chamber 12 to pass through the multitude of guide vanes and rotor blades, and drives the generator 15 coupled to the rotor 14.

[0054] Furthermore, in turbine 13, as in Fig. As shown in Figure 2, turbine guide vanes 21 are configured such that airfoils 23 are fixed at their hub sides by inner fairings 25 and at their tip sides by outer fairings 27. Turbine rotor blades 41 are configured such that the bases of airfoils 43 are fixed by platforms 45. The outer fairings 27 and ring segments 50, which are arranged at the tip sides of the rotor blades 41, are each supported by a housing (turbine housing) 30 via heat-insulating rings 35, and the inner fairings 25 are supported by support rings 31. Thus, a fuel gas flow path 32, through which the fuel gas FG flows, is formed along the axial direction Da as a space enclosed by the inner fairing 25, the outer fairing 27, the platforms 45, and the ring segments 50.

[0055] The inner lining 25, the outer lining 27, and the ring segments 50 each function as gas path surface formation elements. The gas path surface formation elements divide the fuel gas flow path 32 and have a gas path surface on which the fuel gas FG makes contact.

[0056] The combustion chamber 12, the rotor blades 41 (for example, the platforms 45), the guide vanes 21 (for example, the inner shroud 25 and the outer shroud 27), the ring segments 50, and the like are high-temperature components used in a high-temperature environment where the fuel gas FG comes into contact with it and must be cooled by a cooling medium. The following description presents a cooling structure of the ring segment 50 as an example of a cooling structure for this high-temperature component.

[0057] Fig. Figure 3 shows a schematic top view of one of the segment bodies 51, which form a corresponding one of the ring segments 50 when viewed from an outside in the radial direction Dr, and a schematic side view of the segment body 51 when viewed from a downstream side in the rotation direction R of the rotor 14 towards an upstream side in the rotation direction R along the circumferential direction Dc according to some embodiments. Fig. 4 is a cross-sectional view along the line A4-A4 in Fig. 3. Fig. Figure 3 represents the structure of segment body 51 in a simplified form. Therefore, it omits Fig. 3 for example, the description of a hook or the like for attaching the segment body 51 to the thermal insulation ring 35.

[0058] The ring segments 50 according to some embodiments are each formed by the plurality of segment bodies 51, which are annular in the circumferential direction Dc. Each segment body 51 comprises as a main component a body 52, which internally forms the cooling flow paths. As in Fig. As shown in Figure 2, the segment body 51 is arranged such that an inner surface 52a faces the fuel gas flow path 32 in the radial direction Dr, in which the fuel gas FG flows. On the inside of the segment body 51 in the radial direction Dr, the rotor blades 41, which rotate around the rotor 14, are arranged at regular intervals. To prevent thermal damage from the high-temperature fuel gas FG, a plurality of axial channels (cooling channels) 60, extending in the axial direction Da, are formed in the segment body 51.

[0059] The multitude of cooling channels 60 are arranged parallel in the circumferential direction Dc.

[0060] In some embodiments, the circumferential direction Dc in the cooling channels 60 is referred to as a width direction of the cooling channels 60. Furthermore, in some embodiments, the radial direction Dr, orthogonal to the width direction in the cooling channels 60, is referred to as a height direction of the cooling channels 60.

[0061] Although not shown, according to one embodiment, the gas turbine 10 is configured such that cooling air CA is supplied to each segment body 51 from the side of an outer surface 52b, according to some embodiments. The cooling air CA supplied to the segment body 51 convection-cools the body 52 of the segment body 51 by flowing through the cooling channels 60 and being expelled into the fuel gas FG.

[0062] The cooling structure of the segment body 51 is described below according to some exemplary embodiments.

[0063] Each of the cooling channels 60, according to some embodiments, is connected at an upstream end to a cooling air distributor 55. Each of the cooling channels 60, according to some embodiments, internally forms a partition 70 to divide the cooling channel 60 into a plurality of distributor flow channels 63 radiating from the center. In some embodiments, the partition 70 divides the cooling channel 60 into a pair of distributor flow channels 63 radiating from the center in the width direction of the cooling channel 60.

[0064] In the cooling channel 60 according to some embodiments, i.e., a section upstream of the partition 70 and the distributor flow channels 63, the cross-sectional shape of the cooling channel 60, when viewed from the direction of extension of the cooling channel 60, can be rectangular, circular, polygonal (other than rectangular), or oval. Furthermore, the cross-sectional shapes of the flow channels can differ between the distributor flow channel 63 and the section upstream of the partition 70 in the cooling channel 60. That is, the cross-sectional shape of the flow channel in the section upstream of the partition 70 can be rectangular, and the cross-sectional shape of the flow channel in each distributor flow channel 63 can be circular.Furthermore, the flow channel cross-sectional shape in each distributor flow channel 63 can be a shape obtained by dividing a circle or an oval into halves by a corresponding partition 70.

[0065] The cooling channel 60 cools the segment body 51 by cooling an inner wall surface of the cooling channel 60. Thus, the cooling channel 60 has a length that is at least five times greater than its equivalent diameter. The equivalent diameter of the cooling channel 60 is the diameter of a flow path when the cooling channel 60 is replaced by a circular flow path that is equivalent with respect to the flow of cooling air CA, provided the cross-sectional shape of the cooling channel 60 is a non-circular shape.

[0066] Each of the plurality of distributor flow channels 63 is connected at a downstream end 65 to a headpiece 80. In some embodiments, for example, the respective downstream ends 65 of the six distributor flow channels 63 in the three adjacent cooling channels 60 are connected to an upstream inner wall 81 of one headpiece 80. In some embodiments, the plurality of headpieces 80 is formed in the segment body 51.

[0067] Each headpiece 80 is a cuboid space enclosed by the upstream inner wall 81 and a downstream inner wall 82, which represent a pair of walls facing in the axial direction Da, lateral inner walls 83, 84, which represent a pair of walls facing in the circumferential direction Dc, and inner walls (not shown) which represent a pair of walls facing in the radial direction Dr.

[0068] In the downstream inner wall 82 of each headpiece 80, at least one outlet channel 110 is formed for expelling the cooling air CA flowing into the headpiece 80 to the outside of the headpiece 80, i.e., the outside of the segment body 51. In the Fig. In the embodiment shown in Figure 3, an outlet channel 110 is formed in each head piece 80 in the vicinity of the center of the downstream inner wall 82 in the circumferential direction Dc. The outlet channel 110 opens into the fuel gas FG at a downstream end 53 of the segment body 51 in the axial direction Da.

[0069] In some embodiments, the segment body 51 comprises a plurality of cooling channel groups 60, each comprising the one headpiece 80, the three cooling channels 60 connected to the headpiece 80 at their respective downstream ends, and the one outlet channel 110 connected to the headpiece 80.

[0070] The cooling air CA supplied to the segment body 51 from the outside is fed to the cooling air distributor 55 and then distributed by the cooling air distributor 55 to each cooling channel 60. The cooling air CA distributed to each cooling channel 60 is divided by the partition 70 and flows into the respective distributor flow channels 63. The cooling air CA flowing into the respective distributor flow channels 63 is collected in each headpiece 80 and expelled from the outlet channel 110 to the outside of the segment body 51.

[0071] In a machine such as the gas turbine 10, which is operated by a high-temperature working gas, heat loss through cooling generally leads to a reduction in the machine's thermal efficiency. Therefore, it is desirable that a high-temperature component be cooled efficiently with as little cooling medium as possible. For this reason, it is preferable that the cross-sectional area of ​​the flow channel in the cooling channel 60 be no larger than necessary.

[0072] However, if the cross-sectional area of ​​the flow channel is small, the dimensional accuracy of the cooling channel 60 tends to decrease due to a manufacturing limitation of the segment body 51, which serves as the high-temperature component, which can reduce the accuracy of the flow rate of the cooling air CA in the cooling channel 60.

[0073] If the accuracy of the cooling air flow rate CA in the cooling duct 60 is reduced, and the cooling air flow rate CA is greater than a defined flow rate, more heat than required will be extracted by the cooling air CA, which can reduce the thermal efficiency of the gas turbine 10. Furthermore, if the cooling air flow rate CA is less than the defined flow rate, the segment body 51 can be damaged by faulty cooling.

[0074] In view of the foregoing, an object of at least one embodiment of the present invention is to provide the high-temperature component which is able to avoid a deficiency in cooling capacity while suppressing excessive cooling.

[0075] Thus, in some embodiments, the deficiency in cooling capacity is avoided while excessive cooling is suppressed by configuring the cooling structure described below in the segment body 51.

[0076] Fig. Figure 5 is an enlarged view of the area around the headpiece 80 in Fig. 4.

[0077] In some embodiments, the segment body 51, as in Fig. As shown in Figures 3-5, the number of outlet channels 110 connected to the single headpiece 80 is less than the number of a plurality of cooling channels 60 connected to the single headpiece 80. For example, in some embodiments, the six cooling channels 60 (six distributor flow channels 63), as shown in Figure 3-5, are less than the number of multiple cooling channels 60 connected to the single headpiece 80. Fig. 3-5 shown, which are divided by the partitions 70 and the one outlet channel 110, each connected to the one headpiece 80.

[0078] In some embodiments, the outlet channel comprises 110, as shown in Fig. Figure 5 shows an upstream region 111 and a downstream region 115. In the upstream region 111, a reduced section of a flow channel cross-sectional area 113 is formed, in which the flow channel cross-sectional area is gradually reduced towards a downstream side. In the downstream region 115, a minimal flow channel cross-sectional area section 117 is formed, in which the flow channel cross-sectional area is minimal.

[0079] In some embodiments, the cross-sectional shape of the flow channel 110, viewed from the direction of extension of the outlet channel 110, is circular in both the upstream region 111 and the downstream region 115. However, the cross-sectional shape of the flow channel 110 can be rectangular, polygonal (other than rectangular), or oval in both the upstream region 111 and the downstream region 115. Furthermore, the types of cross-sectional shapes of the flow channel can differ between the upstream region 111 and the downstream region 115. That is, the cross-sectional shape of the flow channel in the upstream area 111 can be rectangular, and the cross-sectional shape of the flow channel in the downstream area 115 can be circular.

[0080] Even when considering the case where the flow channel cross-sectional shape in the downstream region 115 is a shape other than the circular shape, the following description is made by the equivalent diameter of the minimum flow channel cross-sectional area section 117 when the size of the flow path in the downstream region 115 is mentioned (minimal flow channel cross-sectional area section 117).

[0081] The equivalent diameter of the minimum flow channel cross-sectional area section 117 is the diameter of the minimum flow channel cross-sectional area section 117 when the flow path is replaced with a circular flow path equivalent with respect to the cooling air flow CA, provided the cross-sectional shape of the minimum flow channel cross-sectional area section 117 is a shape other than circular. If the cross-sectional shape of the minimum flow channel cross-sectional area section 117 is circular, the equivalent diameter of the minimum flow channel cross-sectional area section 117 is the diameter of the minimum flow channel cross-sectional area section 117.

[0082] In some embodiments, the respective minimum flow channel cross-sectional areas SBmin of the outlet channels 110 in the segment body 51 are not smaller than the respective flow channel cross-sectional areas SA of the plurality of cooling channels 60 (distributor flow channels 63) in a connection 67 between the head piece 80 and the cooling channels 60.

[0083] In some embodiments, the segment body 51, as in Fig. Figures 3-5 show the respective minimum flow channel cross-sectional areas SBmin less than a sum ΣSA of the respective flow channel cross-sectional areas SA of the plurality of cooling channels 60 (distributor flow channels 63) which are connected to the one headpiece 80 in the connection 67.

[0084] If no fewer than two outlet channels 110 are connected to the one headpiece 80, the respective minimum flow channel cross-sectional areas SBmin of the outlet channels 110 connected to the one headpiece 80 are not smaller than the respective flow channel cross-sectional areas SA of the plurality of cooling channels 60 in the connection 67.

[0085] Furthermore, if no fewer than two outlet channels 110 are connected to the one headpiece 80, the sum ΣSBmin of the respective minimum flow channel cross-sectional areas SBmin of the outlet channels 110 connected to the one headpiece 80 is less than the sum ΣSA of the respective flow channel cross-sectional areas SA of the plurality of cooling channels 60 connected to the one headpiece 80 in the connection 67.

[0086] As described below, the segment body 51 can be formed, for example, by an additive manufacturing process of a metal or a precision casting process. Thus, the dimensional accuracy of the cooling channel 60 tends to decrease due to a manufacturing limitation of the segment body 51 if the flow channel cross-sectional area SA of the cooling channel 60 is small.

[0087] In the event that the flow rate of the cooling air CA flowing through each of the plurality of cooling channels 60 is determined by each of the flow channel cross-sectional areas SA of the plurality of cooling channels 60, if the flow channel cross-sectional area SA is small, the dimensional accuracy of the cooling channels 60 is reduced as described above, which may reduce the accuracy of the flow rate of the cooling air CA in the cooling channels 60.

[0088] In contrast, with the segment body 51, according to some embodiments, it is possible to define the flow rate of the cooling air CA in the plurality of cooling channels 60 by the minimum flow channel cross-sectional areas SBmin of the outlet channels 110, since the sum ΣSBmin of the respective minimum flow channel cross-sectional areas SBmin of the one or more outlet channels 110 is smaller than the sum ΣSA of the respective flow channel cross-sectional areas SA of the plurality of cooling channels 60 in the connection 67. Thus, the flow channel cross-sectional area SA in each of the plurality of cooling channels 60 does not need to be reduced more than necessary to control the flow rate of the cooling air CA, thereby improving the dimensional accuracy of the cooling channels 60 and making it possible to suppress changes in the flow rate of the cooling air CA among the plurality of cooling channels 60.Therefore, it is possible to avoid a lack of cooling capacity while suppressing excessive cooling.

[0089] Furthermore, according to some embodiments, the segment body 51 easily ensures the dimensional accuracy of the outlet channel 110 in the radial direction, and blockage in the outlet channel 110 by a foreign substance hardly occurs, since the respective minimum flow channel cross-sectional areas SBmin of one or more outlet channels 110 are not smaller than the respective flow channel cross-sectional areas SA of the plurality of cooling channels 60 in the connection 67.

[0090] Furthermore, according to some embodiments, it is possible with the segment body 51 to reduce a section in which accuracy of the flow channel cross-sectional area, i.e. the dimensional accuracy of the channel, is to be ensured, and to suppress manufacturing costs of the segment body 51, since the one or more outlet channels 110 represent a smaller number than the multitude of cooling channels 60 with regard to managing the flow rate of the cooling air CA.

[0091] In some embodiments, the segment body 51, as in Fig. Figure 5 shows a separation distance Ld between the upstream inner wall 81 and the downstream inner wall 82 of the headpiece 80, i.e. a length between the upstream end and the downstream end of the headpiece 80 at least once and at most three times greater than an equivalent diameter DBmin of the downstream region 115, which is a region in which the flow channel cross-sectional area of ​​the outlet channel 110 is minimal.

[0092] If the upstream inner wall 81, i.e., connection positions between the headpiece 80 and the respective downstream ends 65 of the plurality of cooling channels 60, and the downstream inner wall 82, i.e., a connection position between the headpiece 80 and an upstream end 110a of the outlet channel 110, are too close together, the difference in the flow rate of the cooling air CA between the cooling channel 60, whose distance between the downstream end 65 of the cooling channel 60 and the upstream end 110a of the outlet channel 110 is small, and the cooling channel 60, whose distance between the downstream end 65 and the upstream end 110a is large, increases.

[0093] In contrast, according to some embodiments, it is possible with the segment body 51 to suppress the change in the flow rate of the cooling air CA under the plurality of cooling channels 60, since the upstream inner wall 81 and the downstream inner wall 82 are separated from each other by a distance that is at least once greater than the equivalent diameter DBmin described above.

[0094] Furthermore, since the respective downstream ends 65 of the plurality of cooling channels 60 are connected to the headpiece 80, the volume in the headpiece 80 increases, and the flow velocity of the cooling air CA in the headpiece 80 decreases, thereby reducing the heat transfer coefficient CA to the cooling air. Consequently, the cooling capacity in the headpiece 80 can be reduced, and thus it is preferable that the separation distance Ld between the upstream inner wall 81 and the downstream inner wall 82 is not large.

[0095] In this respect, according to some embodiments, it is possible with the segment body 51 to suppress the occurrence of a region in which the cooling capacity in the segment body 51 is defective, since the separation distance Ld between the upstream inner wall 81 and the downstream inner wall 82 is at most three times larger than the equivalent diameter DBmin described above.

[0096] Furthermore, it is possible to suppress a reduction in the thickness of the segment body 51 by suppressing the volume of the headpiece 80, i.e., the volume of an interior of the segment body 51, if the separation distance Ld between the upstream inner wall 81 and the downstream inner wall 82 is at most three times larger than the equivalent diameter DBmin described above.

[0097] In the segment body 51 according to some embodiments, the outlet channel 110 comprises the reduced section of a flow channel cross-sectional area 113, in which the flow channel cross-sectional area of ​​the outlet channel 110 is gradually reduced in the direction of the downstream side.

[0098] Thus, by setting a dimension in a direction orthogonal to the extension direction of the outlet channel 110 from the downstream side of the reduced section of the flow channel cross-sectional area 113, the minimum flow channel cross-sectional area SBmin of the outlet channel 110 is easily set. Therefore, it is possible to control the flow rate of the cooling air CA as long as the dimension is controlled in the direction orthogonal to the extension direction of the outlet channel 110 downstream of the outlet channel 110. This makes it possible to define a range in which the accuracy of the flow channel cross-sectional area, i.e., the dimensional accuracy of the channel, is to be ensured, and to suppress the manufacturing costs of the segment body 51.

[0099] Since the reduced section of the flow channel cross-sectional area 113 is formed in the upstream region 111, as described below, the inner diameter of a subsection leading back to the upstream side from the downstream end 110b is kept constant by machining the outlet channel 110 with a triangular drill from the downstream end 110b towards the upstream end 110a of the outlet channel 110, and the section becomes the downstream region 115. Therefore, it is possible to easily form the minimum flow channel cross-sectional area section 117 in the downstream region 115.

[0100] In the segment body 51 according to some embodiments, the roughness of an inner wall surface 110c of the outlet channel 110 is no greater than the roughness of the respective inner wall surfaces 60a of the plurality of cooling channels 60 in a region where the flow channel cross-sectional area of ​​the outlet channel 110 is minimal. That is, in the segment body 51 according to some embodiments, the roughness of an inner wall surface 115a in the downstream region 115 is no greater than the roughness of the respective inner wall surfaces 60a of the plurality of cooling channels 60.

[0101] Since the inner wall surface 110c of the outlet channel 110 has the roughness described above, the change in pressure loss in the outlet channel 110 is small, thus making it possible to improve the control accuracy of the cooling air flow rate CA. Furthermore, since the inner wall surface 110c of the outlet channel 110 has the roughness described above, foreign substances can easily pass through the outlet channel 110, thereby reducing the risk of clogging.

[0102] In the segment body 51 according to some embodiments, the roughness of an inner wall surface 111a in the upstream region 111 must not be less than or equal to the roughness of the respective inner wall surfaces 60a of the plurality of cooling channels 60.

[0103] For example, in some embodiments, the inner wall surface 110c of the outlet channel 110 has a mean-line average roughness that is not greater than 10 µm in the downstream region 115. Furthermore, in some embodiments, the inner wall surfaces 60a of the plurality of cooling channels 60 each have a mean-line average roughness Ra that is not less than 10 µm and not greater than 20 µm.

[0104] With the segmented body 51 according to some embodiments, it is possible to improve the cooling performance in the cooling channels 60, since the inner wall surfaces 60c of the plurality of cooling channels 60 each exhibit the roughness described above. Furthermore, with the segmented body 51 according to some embodiments, it is possible to suppress changes in the pressure drop in the outlet channel 110 and to ensure that the foreign substance flows easily through the outlet channel 110, thereby reducing the risk of clogging of the outlet channel 110, since an inner wall surface 115c of the downstream region 115 in the outlet channel 110 exhibits the roughness described above.

[0105] In the segment body 51 according to some embodiments, the walls forming the plurality of cooling channels 60, i.e. the partition walls 70, each have chamfered corners 75 at the downstream ends 65 of the cooling channels 60.

[0106] The partitions 70, which also each serve as the walls forming the plurality of cooling channels 60 (distributor flow channels 63), can each have the smallest possible wall thickness, i.e., dimension of the partition 70 in the circumferential direction Dc, as required to improve heat transfer performance. In this case, the shape of the corner may be lost if the segment body 51 is formed by, for example, precision casting or additive manufacturing of a metal, and if subsequent heat treatment is carried out, provided the corner 75 has a shape that is not chamfered at the downstream end 65 of the cooling channel 60 (distributor flow channel 63). If the shape of the corner is lost, a negative effect is transmitted to the flow of the cooling air CA passing through the cooling channel 60, which may reduce the cooling performance.

[0107] In contrast, with the segment body 51, according to some embodiments, it is possible to suppress the negative effect caused by the loss of shape of the corner 75 described above, since the corner 75 is chamfered at the downstream end 65 of the cooling channel 60.

[0108] For example, one outlet channel 110 is in some embodiments, as in Fig. 3-5 shown, connected to the one headpiece 80.

[0109] As described above, with regard to managing the flow rate of the cooling air CA, it is desirable to reduce the section where the accuracy of the flow channel cross-sectional area, i.e., the dimensional accuracy of the channel, is to be ensured. In this respect, according to some in Fig. In the embodiments shown in 3-5, it is possible to reduce the section in which the dimensional accuracy of the channel is to be ensured and to suppress the manufacturing costs of the segment body 51, since one outlet channel 110 is connected to one head piece 80. (Manufacturing process for segment body 51)

[0110] A manufacturing process for the segment body 51 described above, according to several exemplary embodiments, is described below. The segment body 51, according to some exemplary embodiments, can be manufactured, for example, by the additive manufacturing process of a metal or by precision casting. Fig. Figure 6 is a flowchart showing an example of a manufacturing procedure for the case where the segment body 51 is produced by the additive manufacturing process of a metal according to some embodiments. The manufacturing process for the segment body 51 according to some embodiments comprises a cooling channel formation step S10, a headpiece formation step S20, an outlet channel formation step S30, and an outlet channel cutting step S40.

[0111] A forming process for the segment body 51 according to some embodiments can be, for example, powder bed melting, metal deposition, binder spraying, or a process other than those described above. The following description presents a case in which the forming process for the segment body 51 according to some embodiments is, for example, powder bed melting or metal deposition.

[0112] Cooling channel formation step S10 is a step for forming the plurality of cooling channels 60 through which the cooling air CA can flow. Cooling channel formation step S10 includes, for example, forming the segment body 51 up to the respective downstream ends 65 of the cooling channels 60 by laminating the base powder from the upstream side in the axial direction Da towards the downstream side in the axial direction Da.

[0113] The headpiece formation step S20 is a step for forming the headpiece connected to the respective downstream ends of the plurality of cooling channels. Following the cooling channel formation step S10, the headpiece formation step S20 comprises forming the segment body 51 up to the downstream inner wall 82 of the headpiece 80 by laminating the base powder from the upstream side in the axial direction Da towards the downstream side in the axial direction Da.

[0114] The outlet channel training step S30 is a step for training one or more outlet channels 110 for expelling the cooling air CA flowing in the headpiece 80 to the outside of the headpiece 80. Following the headpiece training step S20, the outlet channel training step S30 comprises training the segment body 51 up to the downstream end 110b of the outlet channel 110 by laminating the base powder from the upstream side in the axial direction Da towards the downstream side in the axial direction Da.

[0115] The outlet channel training step S30 includes training the outlet channel 110 to encompass the reduced section of the flow channel cross-sectional area 113, in which the flow channel cross-sectional area of ​​the outlet channel 110 is gradually reduced towards the downstream side.

[0116] Fig. Figure 7 is a view to describe the outlet channel cutting step S40 described below. Fig. Figure 7 shows a downstream shape of the outlet channel 110 by means of double-dotted catenary lines, before it is cut with a triangular drill 19 in the outlet channel cutting step S40, and the triangular drill 19.

[0117] The outlet channel formation step S30 according to some embodiments comprises forming the downstream side of the outlet channel 110 such that a dimension in the direction orthogonal to the extension direction of the outlet channel 110 on the downstream side of the outlet channel 110 is smaller than a diameter Dd of the triangular drill 19. That is, the outlet channel formation step S30 according to some embodiments comprises forming the reduced section of the flow channel cross-sectional area 113 such that a dimension M in the direction orthogonal to the extension direction of the outlet channel 110 on the most downstream side of the reduced section of the flow channel cross-sectional area 113 is smaller than the diameter Dd of the triangular drill 19.

[0118] The outlet channel cutting step S40 is a step for machining at least a portion of the inner wall surface 110c of the outlet channel 110. Specifically, the outlet channel cutting step S40 is a step for cutting the outlet channel 110 with the triangular drill 19. The outlet channel cutting step S40 comprises machining the outlet channel 110 from the downstream end 110b towards the upstream end 110a of the outlet channel 110 with the triangular drill 19. Consequently, the inner diameter of the section extending back to the upstream side from the downstream end 110b remains constant, and the section becomes the downstream region 115.

[0119] The cooling channel formation step S10 and the headpiece formation step S20 do not necessarily have to be carried out using the additive manufacturing process for metal, but can also be carried out using the precision casting process. In that case, the outlet channel formation step S30 can be carried out using the additive manufacturing process for metal. Additionally, the process from cooling channel formation step S10 to outlet channel formation step S30 can be carried out using the precision casting process.

[0120] In the manufacturing process for the segment body 51 according to some embodiments, the segment body 51 is designed such that the number of outlet channels 110 connected to the one head piece 80 is less than the number of a plurality of cooling channels 60 connected to the one head piece 80.

[0121] Furthermore, in the manufacturing process for the segment body 51 according to some embodiments, the segment body 51 is designed such that the respective minimum flow channel cross-sectional areas SBmin of the outlet channel 110 are not smaller than the respective flow channel cross-sectional areas SA of the plurality of cooling channels 60 (distributor flow channels 63) in the connection 67 between the head piece 80 and the cooling channels 60.

[0122] Furthermore, in the manufacturing process for the segment body 51 according to some embodiments, the segment body 51 is designed such that the respective minimum flow channel cross-sectional areas SBmin of the outlet channels 110 are smaller than the sum ΣSA of the respective flow channel cross-sectional areas SA of the plurality of cooling channels 60 (distributor flow channels 63) that are connected to the one head piece 80 in the connection 67.

[0123] If the segment body 51 is designed such that no fewer than two outlet channels 110 are connected to the one head piece 80, the segment body 51 is designed such that the respective minimum flow channel cross-sectional areas SBmin of the outlet channels 110 connected to the one head piece 80 are not smaller than the respective flow channel cross-sectional areas SA of the plurality of cooling channels 60 in the connection 67.

[0124] Furthermore, if the segment body 51 is designed such that no fewer than two outlet channels 110 are connected to the one head piece 80, the segment body 51 is designed such that the sum ΣSBmin of the respective minimum flow channel cross-sectional areas SBmin of the outlet channels 110 connected to the one head piece 80 is smaller than the sum ΣSA of the respective flow channel cross-sectional areas SA of the plurality of cooling channels 60 connected to the one head piece 80 in the connection 67.

[0125] With the manufacturing process for the segment body 51 according to some embodiments, it is possible to define the flow rate of the cooling air CA in the plurality of cooling channels 60 by the minimum flow channel cross-sectional areas SBmin of the outlet channels 110, since the sum ΣSBmin of the respective minimum flow channel cross-sectional areas SBmin of one or more outlet channels 110 is smaller than the sum ΣSA of the respective flow channel cross-sectional areas SA of the plurality of cooling channels 60 in the connection 67. Thus, in each of the plurality of cooling channels 60, the flow channel cross-sectional area does not need to be reduced more than necessary to control the flow rate of the cooling air CA, thereby improving the dimensional accuracy of the cooling channels 60 and making it possible to suppress changes in the flow rate of the cooling air CA among the plurality of cooling channels 60.Therefore, it is possible to avoid a lack of cooling capacity while suppressing excessive cooling.

[0126] Furthermore, the manufacturing process for the segment body 51 according to some embodiments easily ensures the dimensional accuracy of the outlet channel 110, and clogging in the outlet channel 110 by the foreign substance hardly occurs, since the respective minimum flow channel cross-sectional areas SBmin of one or more outlet channels 110 cannot be smaller than the respective flow channel cross-sectional areas SA of the plurality of cooling channels 60 in the connection 67.

[0127] Furthermore, according to some embodiments, the manufacturing process for the segment body 51 makes it possible to reduce the section in which the accuracy of the flow channel cross-sectional area, i.e., the dimensional accuracy of the channel, is to be ensured, and to reduce the manufacturing costs of the segment body 51, since the one or more outlet channels 110 have a smaller number than the multitude of cooling channels 60 with regard to managing the flow rate of the cooling air CA.

[0128] With the manufacturing process for the segment body 51 according to some embodiments, it is only necessary to manage the dimensional accuracy of the most downstream region in the reduced section of the flow channel cross-sectional area 113, since the outlet channel 110 is designed such that the reduced section of the flow channel cross-sectional area 113 has the minimum flow channel cross-sectional area in the outlet channel 110 with respect to managing the flow rate of the cooling air CA. Thus, it is possible to limit the area in which the accuracy of the flow channel cross-sectional area, i.e., the dimensional accuracy of the channel, is to be ensured, and to reduce the manufacturing costs of the segment body 51.

[0129] The manufacturing process for the segment body 51 according to some embodiments makes it possible to reduce the manufacturing costs of the segment body 51 compared to the case where the outlet channel 110 is formed by machining alone. Furthermore, the manufacturing process for the segment body 51 according to some embodiments makes it possible to improve the dimensional accuracy of the inner wall surface 110c of the outlet channel 110 and to improve the control accuracy of the cooling air flow rate CA compared to the case where the outlet channel 110 is formed by the additive manufacturing process of a metal or the precision casting process alone.Furthermore, according to some embodiments, the manufacturing process for the segment body 51 makes it possible to adjust the dimension of the inner wall surface 110c of the outlet channel 110 while checking the flow rate of the cooling air CA, thus making it possible to suppress an excess or deficiency of the flow rate of the cooling air CA.

[0130] With the manufacturing process for the segment body 51 according to some embodiments, the segment body 51 is easily manufactured, since it is possible to define the dimension of the inner wall surface 110c of the outlet channel 110, or in particular an inner diameter Di of the minimum flow channel cross-sectional area section 117 by the diameter Dd of the triangular drill 19.

[0131] By carrying out the manufacturing process for the segment body 51 according to some embodiments, it is possible to control the flow rate of the cooling air CA in the segment body 51. That is, a flow rate control method for the cooling air CA in the segment body 51 according to some embodiments described above comprises the cooling channel formation step S10, the headpiece formation step S20, the outlet channel formation step S30, and the outlet channel cutting step S40.

[0132] With the flow rate control method for the cooling air CA according to some embodiments, the flow rate of the cooling air CA is easily controlled, since it is possible to define the dimension of the inner wall area 110c of the outlet channel 110 (the inner diameter Di of the minimum flow channel cross-sectional area section 117) by the diameter Dd of the triangular drill 19. Therefore, it is possible to easily avoid a lack of cooling capacity while suppressing excessive cooling.

[0133] In the flow rate control method for the cooling air CA according to some embodiments, the cooling channel training step S10 comprises training the cooling channels 60 contained in each of the plurality of cooling channel groups 6.

[0134] Furthermore, the headpiece formation step S20 in the flow rate control method for the cooling air CA according to some embodiments includes forming the headpieces 80 contained in each of the plurality of cooling channel groups 6.

[0135] In the flow rate control method for the cooling air CA according to some embodiments, the outlet channel training step S30 includes training the outlet channels 110 contained in each of the plurality of cooling channel groups 6.

[0136] In the flow rate control method for the cooling air CA according to some embodiments, the outlet channel cutting step S40 comprises cutting the outlet channels 110 contained in each of the plurality of cooling channel groups 6 with the triangular drill 19.

[0137] Thus, it is possible to define the dimension of the inner wall surface 110c of each outlet channel 110 (the inner diameter Di of the minimum flow channel cross-sectional area section 117) by the diameter Dd of the triangular drill 19, thereby easily suppressing the change in the flow rate of the cooling air CA under the multitude of cooling channel groups 6.

[0138] For example, in some of the embodiments described above, the description has been given by taking the ring segment 50 as an example of the high-temperature component that must be cooled by the cooling medium. However, the present invention is not limited to this, but is also applicable to other high-temperature components, such as the combustion chamber 12, the rotor blade 41 (such as the platform 45), the guide vane 21 (such as the inner lining 25 and the outer lining 27), and the like. Furthermore, the high-temperature component applicable to the present invention is not limited to the components in the gas turbine 10, but can also be a component in a turbomachine other than the gas turbine 10. Reference symbol list 6 Cooling channel group 10 Gas turbine 12 Combustion chamber 13 Turbine 21 Turbine guide vane (guide vane) 41 Turbine rotor blade (rotor blade) 50 ring segment 51 segment bodies 52 bodies 52b External surface (area to be heated) 60 Axial channel (cooling channel) 63 Distributor flow channel 65 Downstream end 67 connection 70 partition wall 80 Headpiece 81 Upstream interior wall 82 Downstream interior wall 110 Outlet channel 111 Upstream area 113 Reduced section of a flow channel cross-sectional area 115 Downstream area 117 Minimum flow channel cross-sectional area section

Claims

[1] A high-temperature component used for a turbomachine which must be cooled by a cooling medium, wherein it has: a multitude of cooling channels (60) through which the cooling medium can flow; a headpiece (80) which is connected to the respective downstream ends (65) of the plurality of cooling channels (60); and one or more outlet channels (110) for expelling the cooling medium flowing into the headpiece (80) to the outside of the headpiece (80), wherein the one or more outlet channels (110) are present in fewer numbers than the multitude of cooling channels (60), wherein the respective minimum flow channel cross-sectional areas (SBmin) of the one or more outlet channels (110) are not smaller than the respective flow channel cross-sectional areas (SA) of the plurality of cooling channels (60) in a connection between the headpiece (80) and the cooling channels (60), wherein a sum of the respective minimum flow channel cross-sectional areas (SBmin) of the one or more outlet channels (110) is smaller than a sum of the respective flow channel cross-sectional areas (SA) of the plurality of cooling channels (60) in the connection between the headpiece (80) and the cooling channels (60), wherein the one or more outlet channels (110) each have an inner wall surface (110c) whose mean-line average roughness Ra is not greater than 10 µm in a region (115) where the flow channel cross-sectional area of ​​the outlet channel (110) is minimal, and wherein the plurality of cooling channels (60) each has an inner wall surface (60a) whose mean line average roughness Ra is not less than 10 µm and not greater than 20 µm. [2] A high-temperature component used for a turbomachine which must be cooled by a cooling medium, wherein the high-temperature component has: a multitude of cooling channels (60) through which the cooling medium can flow; a headpiece (80) which is connected to the respective downstream ends (65) of the plurality of cooling channels (60); and one or more outlet channels (110) for expelling the cooling medium flowing into the headpiece (80) to the outside of the headpiece (80), wherein the one or more outlet channels (110) are present in fewer numbers than the multitude of cooling channels (60), wherein the respective minimum flow channel cross-sectional areas (SBmin) of the one or more outlet channels (110) are not smaller than the respective flow channel cross-sectional areas (SA) of the plurality of cooling channels (60) in a connection between the headpiece (80) and the cooling channels (60), wherein a sum of the respective minimum flow channel cross-sectional areas (SBmin) of the one or more outlet channels (110) is smaller than a sum of the respective flow channel cross-sectional areas (SA) of the plurality of cooling channels (60) in the connection between the headpiece (80) and the cooling channels (60), wherein the high-temperature component represents ring segments (50) of a gas turbine (10), each consisting of a plurality of segment bodies (51) arranged in a ring shape along a circumferential direction (Dc), wherein the plurality of segment bodies (51) each has an inner surface (52a) which faces a fuel gas flow path (32) through which a fuel gas (FG) flows, wherein the plurality of cooling channels (60) is each formed in the plurality of segment bodies (51), and wherein one or more outlet channels (110) at respective downstream ends (65) of the plurality of segment bodies (51) are open in an axial direction (Da) into the fuel gas (FG). [3] The high-temperature component according to claim 1 or 2, wherein a separation distance (Ld) between an upstream inner wall (81) and a downstream inner wall (82) of the head piece (80) is at least once and at most three times larger than an equivalent diameter (DBmin) of the region (115) in which the flow channel cross-sectional area of ​​the outlet channel (110) is minimal. [4] The high-temperature component according to one of claims 1-3, wherein the one or more outlet channels (110) each comprise a reduced section of the flow channel cross-sectional area (113) in which the flow channel cross-sectional area of ​​the outlet channel (110) is gradually reduced in the direction of a downstream side. [5] The high-temperature component according to one of claims 1-4, wherein partitions (70) forming the plurality of cooling channels (60) have chamfered corners (75) at downstream ends (65) of the cooling channels (60). [6] The high-temperature component according to any one of claims 1-5, wherein the number of outlet channels (110) is one. [7] A high-temperature component used for a turbomachine with a rotor (14) which must be cooled by a cooling medium, wherein the high-temperature component has: a plurality of cooling channels (60) through which the cooling medium can flow, wherein the plurality of cooling channels (60) extends in an axial direction (Da) of the rotor (14); a headpiece (80) which is connected to the respective downstream ends (65) of the plurality of cooling channels (60); and one or more outlet channels (110) for expelling the cooling medium flowing into the headpiece (80) to the outside of the headpiece (80) along the axial direction (Da), wherein the plurality of cooling channels (60) in the axial direction (Da) each have a longer length dimension than the head piece (80), wherein the plurality of cooling channels (60) each have a longer length dimension than the one or more outlet channels (110) in the axial direction (Da), wherein the one or more outlet channels (110) are present in fewer numbers than the multitude of cooling channels (60), wherein the respective minimum flow channel cross-sectional areas (SBmin) of the one or more outlet channels (110) are not smaller than the respective flow channel cross-sectional areas (SA) of the plurality of cooling channels (60) in a connection between the headpiece (80) and the cooling channels (60), and wherein a sum of the respective minimum flow channel cross-sectional areas (SBmin) of the one or the multiple outlet channels (110) is smaller than a sum of the respective flow channel cross-sectional areas (SA) of the plurality of cooling channels (60) in the connection between the headpiece (80) and the cooling channels (60). [8] A manufacturing process for a high-temperature component used for a turbomachine with a rotor (14) and which must be cooled by a cooling medium, wherein the manufacturing process comprises: a step to form a plurality of cooling channels (60) through which the cooling medium can flow, wherein the plurality of cooling channels (60) extends in an axial direction (Da) of the rotor (14); a step to form a headpiece (80) which is connected to the respective downstream ends (65) of the plurality of cooling channels (60); and a step to form one or more outlet channels (110) for expelling the cooling medium flowing into the headpiece (80) to the outside of the headpiece (80) along the axial direction (Da), wherein the plurality of cooling channels (60) in the axial direction (Da) each have a longer length dimension than the head piece (80), wherein the plurality of cooling channels (60) each have a longer length dimension than the one or more outlet channels (110) in the axial direction (Da), wherein the one or more outlet channels (110) are present in fewer numbers than the multitude of cooling channels (60), wherein the respective minimum flow channel cross-sectional areas (SBmin) of the one or more outlet channels (110) are not smaller than the respective flow channel cross-sectional areas (SA) of the plurality of cooling channels (60) in a connection between the headpiece (80) and the cooling channels (60), and wherein a sum of the respective minimum flow channel cross-sectional areas (SBmin) of the one or the multiple outlet channels (110) is smaller than a sum of the respective flow channel cross-sectional areas (SA) of the plurality of cooling channels (60) in the connection between the headpiece (80) and the cooling channels (60). [9] The manufacturing process for the high-temperature component according to claim 8, wherein the step of forming the one or more outlet channels (110) comprises forming the one or more outlet channels (110) such that each comprises a reduced section of a flow channel cross-sectional area (113) in which the flow channel cross-sectional area of ​​the outlet channel (110) is gradually reduced in the direction of a downstream side. [10] The manufacturing process for the high-temperature component according to claim 8 or 9, wherein the step of forming the one or more outlet channels (110) comprises forming the one or more outlet channels (110) by a process for the additive manufacturing of a metal or a precision casting process, and wherein the method further comprises a step for performing a machining of at least a part of an inner wall surface (110c) of each of the one or more outlet channels (110). [11] The manufacturing process for the high-temperature component according to claim 10, wherein the step of performing a machining operation comprises cutting one or more outlet channels (110) with a drill (19).

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