Assembly of rotary machine

Abstract

To efficiently absorb thermal expansion in an assembly of a rotary machine.SOLUTION: An assembly of a rotary machine according to at least one embodiment of the present disclosure comprises: a first member that has a plurality of first hole parts having female screws formed inside, is formed of a first metallic material with a first linear expansion coefficient, and extends in a circumferential direction; a second member that is bolted to the first member and provided with a plurality of second hole parts, i.e. through-holes, and is formed of a second metallic material different from the first metallic material with a second linear expansion coefficient different from the first linear expansion coefficient; a plurality of bolts that respectively pass through the second hole parts of the second member and are screwed with the first hole parts of the first member; and a third member that is provided between bolt heads and the second member, provided with a plurality of third hole parts, i.e. through-holes, and formed of a third metallic material with a third linear expansion coefficient. An absolute value of a difference between the third linear expansion coefficient and the first linear expansion coefficient is smaller than an absolute value of a difference between the second linear expansion coefficient and the first linear expansion coefficient.SELECTED DRAWING: Figure 3

Description

[Technical field]

[0001] The present disclosure relates to rotary machine assemblies. [Background technology]

[0002] For example, a gas turbine, which is an example of a rotary machine, is composed of a compressor, a combustor, and a turbine. Air taken in from an air intake is compressed by the compressor to become high-temperature, high-pressure compressed air, and fuel is supplied to this compressed air in the combustor to burn it, and the high-temperature, high-pressure combustion gas drives the turbine, which then drives a generator connected to the turbine. In this case, the turbine is composed of multiple stationary vanes and moving blades arranged alternately in a casing, and the moving blades are driven by the combustion gas to rotate an output shaft connected to the generator. The combustion gas that drives the turbine is then converted to static pressure by a diffuser in the exhaust casing before being released into the atmosphere.

[0003] For example, in a turbine, an exhaust chamber is connected downstream of an exhaust casing that houses stationary blades and rotor blades, and an exhaust duct is connected downstream of the exhaust chamber. The connection structure between the exhaust casing and the exhaust chamber, and the connection structure between the exhaust chamber and the exhaust duct are configured to absorb thermal expansion (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0004] [Patent Document 1] JP 2009-203871 A Summary of the Invention [Problem to be solved by the invention]

[0005] However, since there is a tendency for the temperature of the combustion gas to become higher due to the increase in the output and efficiency of gas turbines, it is desired to be able to absorb more of the thermal expansion.

[0006] In view of the above, at least one embodiment of the present disclosure has an object to efficiently absorb thermal expansion in an assembly of a rotating machine. [Means for solving the problem]

[0007] A rotary machine assembly according to at least one embodiment of the present disclosure includes: a first member having a plurality of first holes with female threads formed therein, the first member being made of a first metallic material having a first linear expansion coefficient and extending in a circumferential direction; a second member that is bolted to the first member, that is provided with a plurality of second hole portions that are through holes, and that is made of a second metal material different in type from the first metal material and that has a second linear expansion coefficient that is different from the first linear expansion coefficient; a plurality of bolts each passing through the second hole portion of the second member and screwed into the first hole portion of the first member; a third member provided between the head of the bolt and the second member, the third member having a plurality of third hole portions that are through holes and made of a third metallic material having a third linear expansion coefficient; Equipped with The absolute value of the difference between the third linear expansion coefficient and the first linear expansion coefficient is smaller than the absolute value of the difference between the second linear expansion coefficient and the first linear expansion coefficient. Effect of the Invention

[0008] At least one embodiment of the present disclosure provides for efficient absorption of thermal expansion in a rotating machine assembly. [Brief description of the drawings]

[0009] [Figure 1] FIG. 1 is a schematic diagram of a gas turbine according to some embodiments. [Diagram 2] 1 is a cross-sectional view of a main portion of a gas turbine illustrating a connection structure of an exhaust chamber in the gas turbine according to some embodiments. [Diagram 3] 1 is a cross-sectional view illustrating a connection between an exhaust casing and an exhaust chamber in a gas turbine according to some embodiments. [Figure 4]FIG. 13 is a view of the connecting ring and the exhaust chamber support as seen from the radially outer side. [Diagram 5] FIG. 5 is a view taken along the arrows VV in FIG. 4. [Figure 6] 6 is a view taken along the line VI-VI in FIG. 5. [Figure 7] 5 is a view of the exhaust chamber support as seen from the axial downstream side, corresponding to the view seen from the arrow VV in FIG. 4. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0010] 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 components described as the embodiments or shown in the drawings are merely illustrative examples and are not intended to limit the scope of the present disclosure. For example, expressions expressing relative or absolute configuration, such as "in a certain direction," "along a certain direction," "parallel," "orthogonal," "center," "concentric," or "coaxial," not only strictly express such a configuration, but also express a state in which there is a relative displacement with a tolerance or an angle or distance to the extent that the same function is obtained. For example, expressions indicating that things are in an equal state, such as "identical," "equal," and "homogeneous," not only indicate a state of strict equality, but also indicate a state in which there is a tolerance or a difference to the extent that the same function is obtained. For example, expressions describing shapes such as a rectangular shape or a cylindrical shape do not only refer to rectangular shapes, cylindrical shapes, etc. in the strict geometric sense, but also refer to shapes that include uneven portions, chamfered portions, etc., to the extent that the same effect is obtained. On the other hand, the expressions "comprise," "include," "have," "includes," or "have" of one element are not exclusive expressions excluding the presence of other elements.

[0011] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the exhaust duct connection structure and the gas turbine according to the present invention will be described in detail below with reference to the accompanying drawings. However, the present invention is not limited to these embodiments.

[0012] Fig. 1 is a schematic configuration diagram of a gas turbine according to some embodiments. Fig. 2 is a cross-sectional view of a main part of the turbine, showing a connection structure of an exhaust casing in a gas turbine according to some embodiments. Fig. 3 is a cross-sectional view showing a connection part between an exhaust casing and an exhaust casing in a gas turbine according to some embodiments.

[0013] As shown in FIG. 1, the gas turbine 1 of this embodiment is composed of a compressor 11, a combustor 12, a turbine 13, and an exhaust chamber 14. A generator (not shown) is connected to the gas turbine 1. The compressor 11 has an air intake 15 for taking in air, and is configured by alternately arranging a plurality of stator vanes 17 and rotor blades 18 in a compressor casing 16, and an extraction manifold 19 is provided on the outside thereof. The combustor 12 supplies fuel to the compressed air compressed by the compressor 11, and is combusted by igniting it with a burner. The turbine 13 has a plurality of stator vanes 21 and rotor blades 22 arranged alternately in a turbine casing 20. The exhaust chamber 14 is arranged downstream of the turbine casing 20 via an exhaust casing 27. The exhaust chamber 14 has an exhaust diffuser 23 that is continuous with the turbine 13. A rotor (turbine shaft) 24 is positioned so as to penetrate the center of the compressor 11, the combustor 12, the turbine 13, and the exhaust chamber 14. The rotor 24 has an end on the compressor 11 side rotatably supported by a bearing 25, and an end on the exhaust chamber 14 side rotatably supported by a bearing 26. The rotor 24 is made up of a plurality of stacked disks, each having the rotor blades 18, 22 mounted thereon, and a drive shaft of a generator (not shown) is connected to the end on the exhaust chamber 14 side.

[0014] Therefore, air taken in from the air intake 15 of the compressor 11 passes through a plurality of stator vanes 21 and rotor blades 22 and is compressed to become high-temperature, high-pressure compressed air. A specified fuel is supplied to this compressed air in the combustor 12, and it is burned. Then, high-temperature, high-pressure combustion gas, which is a working fluid produced in the combustor 12, passes through a plurality of stator vanes 21 and rotor blades 22 that constitute the turbine 13, driving and rotating the rotor 24, which in turn drives a generator connected to the rotor 24. The exhaust gas is converted to static pressure in the exhaust diffuser 23 in the exhaust chamber 14 and then released into the atmosphere.

[0015] In the above-mentioned turbine 13, as shown in Fig. 2, there is a turbine casing 20 in which a plurality of stator vanes 21 and rotor blades 22 are alternately arranged, and there is an exhaust casing 27 downstream of the turbine casing 20. The exhaust casing 27 has a cylindrical shape. The exhaust chamber 14 is disposed downstream of the exhaust casing 27 in the flow direction of the exhaust gas. This exhaust chamber 14 has a cylindrical shape. An exhaust duct 31 is disposed downstream of the exhaust chamber 14 in the flow direction of the exhaust gas. The exhaust duct 31 has a cylindrical shape. The exhaust casing 27 and the exhaust chamber 14 are connected by an exhaust chamber support 32 capable of absorbing thermal expansion.

[0016] A cylindrical exhaust diffuser 41 is disposed inside the exhaust casing 27. The exhaust diffuser 41 is configured by connecting a cylindrical outer diffuser 42 and an inner diffuser 43 by a strut shield 44. The strut shields 44 have a hollow structure, such as a cylindrical or elliptical cylindrical shape, and a plurality of strut shields 44 are provided at equal intervals in the circumferential direction of the exhaust diffuser 41. The rotor 24 is rotatably supported on the inner peripheral part of the inner diffuser 43 via a bearing part (not shown). A strut 47 is disposed inside the strut shield 44. One end of the strut 47 is fixed to the exhaust casing 27, and the other end is fixed to a bearing box of the bearing part (not shown).

[0017] The exhaust casing 27 and the exhaust diffuser 41 are connected by a diffuser support 48. This diffuser support 48 has a rectangular shape, extends along the axial direction of the turbine 13, and is arranged in parallel at predetermined intervals in the circumferential direction. When thermal expansion occurs between the exhaust casing 27 and the exhaust diffuser 41 due to a temperature difference, the diffuser support 48 is capable of absorbing the thermal expansion by deforming. The exhaust casing 27 is provided so as to cover the diffuser support 48 from the outside.

[0018] Exhaust chamber 14 is constructed by connecting cylindrical outer cylinder 52 and inner cylinder 53 by follow struts 54, and these follow struts 54 have a hollow structure such as a cylindrical or elliptical cylindrical shape, and a plurality of follow struts 54 are provided at equal intervals around the circumferential direction of exhaust chamber 14. Follow struts 54 open on the outer cylinder 52 side of exhaust chamber 14, and the inside of follow struts 54 communicates with the atmosphere.

[0019] The exhaust casing 27 and the exhaust chamber 14 are connected by an exhaust chamber support 32 . The exhaust diffuser 41 and the exhaust chamber 14 are arranged such that the ends of the outer diffuser 42 and the outer cylinder 52, and the ends of the inner diffuser 43 and the inner cylinder 53 are close to each other and face each other. The outer diffuser 42 and the outer cylinder 52 increase in diameter toward the downstream side in the flow direction of the exhaust gas, while the inner diffuser 43 and the inner cylinder 53 have the same diameter toward the downstream side in the flow direction of the exhaust gas. The end of the exhaust casing 27 located outer circumferentially further than the outer diffuser 42 of the exhaust diffuser 41 is connected to the end of the outer cylinder 52 of the exhaust chamber 14 by the exhaust chamber support 32.

[0020] The exhaust chamber support 32 has a rectangular plate-like portion 32P, which extends along the axial direction of the turbine 13 and is arranged in parallel at a predetermined interval in the circumferential direction. When thermal expansion occurs in the exhaust chamber support 32 due to a temperature difference between the exhaust casing 27 and the exhaust chamber 14, the plate-like portion 32P is deformed to absorb the thermal expansion. Thermal expansion is likely to occur during a transitional period, such as when the turbine 13 is started, or during high loads.

[0021] 3, a connecting ring 55 is fixed to the end of the exhaust casing 27 with bolts 56. The exhaust chamber support 32 has a connecting flange 32a at one end fastened to the connecting ring 55 with bolts 57, and a connecting flange 32b at the other end fastened to the outer casing 52 in the exhaust chamber 14 with bolts (not shown). A gas seal 59 is provided between the downstream end of the exhaust casing 27 and the downstream end of the outer diffuser 42. A gas seal 60 is provided between the connecting ring 55 and the upstream end of the outer casing 52, located inside the exhaust chamber support 32.

[0022] The gas seal 59 serves to keep the cooling air supplied through the inside of the strut shield 44 between the outer diffuser 42 and the exhaust casing 27 .

[0023] A heat insulating material (not shown) is attached to the outer peripheral surface of the exhaust casing 27. Similarly, a heat insulating material (not shown) is attached to the outer peripheral surface of the exhaust chamber 14. The exhaust chamber support 32 is provided outside the outer cylinder 52 of the exhaust chamber 14, and the exhaust chamber support 32 is disposed outside the heat insulating material on the outer peripheral surface of the exhaust chamber 14. The exhaust chamber support 32 can be cooled by outside air.

[0024] The exhaust duct 31 shown in FIG. 2 has a cylindrical shape and is connected to the exhaust chamber 14.

[0025] As described above, in the connection structure of the exhaust chamber, which is an assembly of the rotating machine in this embodiment, the exhaust chamber 14 and the exhaust casing 27, which is located upstream of the exhaust chamber 14 in the exhaust gas flow direction, are connected by an exhaust chamber support 32 capable of absorbing thermal expansion, an insulating material (not shown) is attached to the outer circumferential surface of the exhaust chamber 14, and the exhaust chamber supports 32 are arranged outside the insulating material in the form of a plurality of strips, with one end connected to an end of the exhaust chamber 14 and the other end connected to an end of the exhaust casing 27.

[0026] Therefore, since the exhaust chamber support 32 has a rectangular shape, it can easily deform and efficiently absorb the thermal expansion that occurs between the exhaust chamber 14 and the exhaust casing 27. In addition, since the exhaust chamber support 32 is disposed outside the thermal insulation material, the exhaust chamber support 32 is sufficiently cooled by the outside air. As a result, the thermal stress in the connection portion between the exhaust chamber 14 and the exhaust casing 27, i.e., in the exhaust chamber support 32, can be reduced, thereby improving durability.

[0027] Therefore, since the exhaust chamber support 32 has a rectangular shape, it can be easily deformed and can efficiently absorb thermal expansion that occurs between the exhaust casing 27 and the exhaust chamber 14. Also, since the exhaust chamber support 32 is disposed outside the thermal insulation material, the exhaust chamber support 32 is sufficiently cooled by outside air. As a result, durability can be improved by reducing thermal stress in the connection portion between the exhaust casing 27 and the exhaust chamber 14, i.e., in the exhaust chamber support 32, and as a result, turbine output and efficiency can be improved.

[0028] In the exhaust chamber connection structure thus configured, i.e., in the rotary machine assembly, the connecting ring 55 and the exhaust chamber support 32 are made of different types of metallic materials from the viewpoint of cost, etc. Therefore, when the connecting ring 55 and the exhaust chamber support 32 are heated during operation of the gas turbine 1, the relative positions of the connecting ring 55 and the exhaust chamber support 32 in the circumferential direction about the axis AX of the rotor 24 are shifted due to the difference in linear expansion coefficient between the connecting ring 55 and the exhaust chamber support 32. Therefore, if the connecting flange 32a of the exhaust chamber support 32 is in direct contact with the seating surface of the head of the bolt 57, the head of the bolt 57 is pulled in the circumferential direction due to friction with the connecting flange 32a, and a shear force acts on the bolt 57. Therefore, if the connecting flange 32a of the exhaust chamber support 32 is in direct contact with the seating surface of the head of the bolt 57, the bolt 57 may be damaged.

[0029] Therefore, in the rotary machine assembly according to this embodiment, a washer 70 is disposed between the connecting flange 32a of the exhaust chamber support 32 and the head of the bolt 57. When the linear expansion coefficient α of the connecting ring 55 is defined as a first linear expansion coefficient α1, the linear expansion coefficient α of the exhaust chamber support 32 (connecting flange 32a) is defined as a second linear expansion coefficient α2, and the linear expansion coefficient α of the washer 70 is defined as a third linear expansion coefficient α3, the absolute value of the difference between the third linear expansion coefficient and the first linear expansion coefficient is smaller than the absolute value of the difference between the second linear expansion coefficient and the first linear expansion coefficient.

[0030] That is, the rotary machine assembly 100 according to this embodiment includes a connecting ring 55 as a first member, an exhaust chamber support 32 (connecting flange 32a) as a second member, a washer 70 as a third member, and a plurality of bolts 57. In the rotary machine assembly 100 according to this embodiment, the connecting ring 55 is made of a first metallic material having a first linear expansion coefficient α1, the exhaust chamber support 32 (connecting flange 32a) is made of a second metallic material different from the first metallic material having a second linear expansion coefficient α2 different from the first linear expansion coefficient α1, and the washer 70 is made of a third metallic material having a third linear expansion coefficient α3. The first metallic material, the second metallic material, and the third metallic material are metallic materials such that the absolute value of the difference between the third linear expansion coefficient and the first linear expansion coefficient is smaller than the absolute value of the difference between the second linear expansion coefficient and the first linear expansion coefficient.

[0031] As a result, the difference in thermal expansion between connecting ring 55 and washer 70 is smaller than the difference in thermal expansion between connecting ring 55 and connecting flange 32a. As a result, even if the head of bolt 57 is pulled in the circumferential direction due to friction between the seat surface of the head of bolt 57 and washer 70 and the washer 70 caused by the difference in thermal expansion between connecting ring 55 and washer 70, the possibility of bolt 57 being damaged can be reduced compared to when connecting flange 32a is bolted to connecting ring 55 without washer 70.

[0032] The rotary machine assembly 100 according to this embodiment will be further described below. FIG. 4 is a view of the connecting ring 55 and the exhaust chamber support 32 as viewed from the outside in the radial direction centered on the axis AX of the rotor 24. FIG. 5 is a view taken along the line VV of FIG. FIG. 6 is a view taken along the line VI-VI in FIG. FIG. 7 is a diagram of the exhaust chamber support 32 as viewed from the axial downstream side, and corresponds to a view as viewed in the direction of arrows VV in FIG. In the following description, the direction of the axis AX of the rotor 24 is also referred to as the axial direction, the circumferential direction centered on the axis AX is also simply referred to as the circumferential direction, and the radial direction centered on the axis AX is also simply referred to as the radial direction. In the axial direction, the upstream side in the flow direction of the combustion gas is also referred to as the axial upstream side, and the downstream side in the flow direction of the combustion gas is also referred to as the axial downstream side. Note that the downstream side in the flow direction of the exhaust gas mentioned above is the axial downstream side.

[0033] (Regarding connecting ring 55) The connecting ring 55 is an annular member (flange portion) extending in the circumferential direction. In the rotary machine assembly 100 according to this embodiment, the connecting ring 55 is divided into an upper half and a lower half, each of which extends over half of the circumference in the circumferential direction. 6, the connecting ring 55 is provided with a plurality of first hole portions 55a with female threads 55b formed therein at intervals in the circumferential direction. The connecting ring 55 is also provided with pin holes 55c into which pins 71, which will be described later, are inserted. The pin holes 55c are formed in the connecting ring 55 such that one pin hole 55c is provided for each exhaust chamber support 32.

[0034] The pin holes 55c are provided at circumferential positions such that the number of first hole portions 55a for fixing one exhaust chamber support 32 is the same on one side and the other side in the circumferential direction about the pin hole 55c. In the example shown in Fig. 6, the pin holes 55c are provided at circumferential positions such that the number of first hole portions 55a for fixing one exhaust chamber support 32 is three on each of the one side and the other side in the circumferential direction about the pin hole 55c.

[0035] The material of the connecting ring 55 is, for example, chrome molybdenum steel.

[0036] (Connecting flange 32a) In the rotating machine assembly 100 of this embodiment, the connecting flange 32a is a flange-shaped portion for fixing the exhaust chamber support 32 to the connecting ring 55, and protrudes radially outward from the plate-shaped portion 32P at the axially upstream end of the plate-shaped portion 32P and extends circumferentially. In the rotary machine assembly 100 according to this embodiment, a plurality of exhaust chamber supports 32 are attached to each of the upper and lower halves of the connection ring 55 .

[0037] The connecting flange 32a is provided with a plurality of second holes 32c that axially penetrate the connecting flange 32a at positions that correspond to the first holes 55a of the connecting ring 55 when the connecting flange 32a is attached to the connecting ring 55.

[0038] The connecting flange 32a is provided with a pin hole 32d through which a pin 71, which will be described later, is inserted. The pin hole 32d is provided at a circumferential position such that the number of the second hole portions 32c is the same on one side and the other side of the pin hole 32d in the circumferential direction. In the example shown in Fig. 6, the pin hole 32d is provided at a circumferential position such that the number of the second hole portions 32c is three on each of the one side and the other side of the pin hole 32d in the circumferential direction.

[0039] The material of the connecting flange 32a is, for example, austenitic stainless steel.

[0040] (Washer 70) In the rotary machine assembly 100 according to this embodiment, the washer 70 is a single washer provided between the head 57h of the bolt 57 and the connecting flange 32a, and extends in the circumferential direction. In the rotary machine assembly 100 according to this embodiment, one washer 70 is used to fix one exhaust chamber support 32 to the connecting ring 55.

[0041] The washer 70 has a plurality of third holes 70a that axially penetrate the washer 70 at positions corresponding to the first hole portion 55a of the connecting ring 55 and the second hole portion 32c of the connecting flange 32a when the connecting flange 32a is attached to the connecting ring 55.

[0042] The washer 70 is provided with a pin hole 70b, which is an insertion hole through which a pin 71, which will be described later, is inserted. The pin hole 70b is provided at a circumferential position such that the number of the third hole portions 70a is the same on one side and the other side of the pin hole 70b in the circumferential direction. In the example shown in Fig. 6, the pin hole 70b is provided at a circumferential position such that the number of the third hole portions 70a is three on each of the one side and the other side of the pin hole 70b in the circumferential direction. That is, in the rotary machine assembly 100 according to this embodiment, the pin hole 70b is provided in a central region 70d away from both ends of the washer 70 in the circumferential direction.

[0043] When the exhaust chamber support 32 is attached to the connecting ring 55 with the bolt 57, the axially downstream surface 70c of the washer 70 abuts against the bearing surface 57a of the head 57h of the bolt 57. That is, in the rotating machine assembly 100 according to this embodiment, the connecting flange 32a and the washer 70 are sandwiched between the connecting ring 55 and the head 57h of the bolt 57.

[0044] The material of the washer 70 is, for example, chrome molybdenum steel, which is the same as that of the connecting ring 55. That is, the washer 70 is made of the same type of metal material as the connecting ring 55. As a result, if the connecting ring 55 and the washer 70 are at the same temperature, the difference in thermal expansion between the connecting ring 55 and the washer 70 is eliminated, and the possibility of the bolt 57 being damaged can be reduced. Here, the same type of metallic material refers to metallic materials that have the same standard or product name, such as stainless steel or chrome molybdenum steel, as defined by the material symbols in the Japanese Industrial Standards.

[0045] The material of washer 70 is, for example, the same chrome-molybdenum steel as that of connecting ring 55, but the material may be such that the absolute value of the difference between the linear expansion coefficient of washer 70 (third linear expansion coefficient α3) and the linear expansion coefficient of connecting ring 55 (first linear expansion coefficient α1) is smaller than the absolute value of the difference between the linear expansion coefficient of connecting flange 32a (second linear expansion coefficient α2) and the linear expansion coefficient of connecting ring 55 (first linear expansion coefficient α1).

[0046] (Bolt 57) In the rotary machine assembly 100 according to this embodiment, the bolts 57 are made of, for example, austenitic stainless steel.

[0047] (Pin 71) In the rotating machine assembly 100 according to this embodiment, a pin 71 is provided as a position determining member for determining the relative positions of the connecting ring 55, the connecting flange 32a, and the washer 70. The pin 71 is inserted through the pin hole 55c of the connecting ring 55, the pin hole 32d of the connecting flange 32a, and the pin hole 70b of the washer 70. As a modified example of the pin 71, which is a position defining member, a structure in which a threaded portion is provided on a part or the entire area in the longitudinal direction of the pin 71 may be used. For example, a structure like a reamer bolt may be used in which a screw is screwed into a pin hole of each member or a part of a member. Also, the cross-sectional shape of the pin 71 may not be circular, but may be polygonal, and is not limited to the above structure as long as the relative positions of each member can be defined. As a result, the relative positions of the connecting ring 55, the connecting flange 32a, and the washer 70 are determined by the pin 71, so that the above-mentioned relative positions are less likely to change even if the rotating machine assembly 100 is subjected to repeated heating and cooling cycles, causing repeated thermal expansion and contraction.

[0048] In the rotating machine assembly 100 of this embodiment, the multiple first hole portions 55a, the multiple second hole portions 32c, and the multiple third hole portions 70a are each circumferentially spaced apart, and the washer 70 is formed to extend circumferentially. This makes it possible to rationalize the structure of the assembly 100 in which the connecting flange 32a is pressed and fixed to the connecting ring 55 extending in the circumferential direction by the washer 70.

[0049] In the rotating machine assembly 100 of this embodiment, the washer 70 has a pin hole 70b, which is a through hole, provided in a central region 70d away from both circumferential ends, and the pin 71 is inserted into the pin hole 70b. This makes it possible to reduce the maximum amount of thermal expansion of the washer 70 in the circumferential direction based on the pin hole 70b, compared to when the pin hole 70b is provided near both circumferential ends of the washer 70.

[0050] As shown in FIG. 7, in the rotating machine assembly 100 of this embodiment, among the multiple second hole portions 32c, the hole size (circumferential length L) of the second hole portion 32c located at a first circumferential position may be larger than the hole size (circumferential length L) of the second hole portion located at a second position circumferentially closer to the pin 71 (pin hole 32d) than the first position. Here, when focusing on any two second hole portions 32c on one side and the other side of the pin hole 32d in the circumferential direction, the position of the second hole portion 32c farthest from the pin hole 32d is the first circumferential position, and the position of the other second hole portion 32c is the second circumferential position.

[0051] The difference in thermal expansion between the connecting flange 32a and the connecting ring 55 in the circumferential direction increases with increasing distance from the pin 71 (pin hole 32d) in the circumferential direction. According to the above configuration, the hole size (circumferential length L) of the second hole portion 32c located at the first position is larger than the hole size (circumferential length L) of the second hole portion 32c located at the second position which is circumferentially closer to the pin 71 (pin hole 32d) than the first position, so that even when the assembly 100 is heated, the second hole portion 32c located at the first position is less likely to come into contact with the bolt 57.

[0052] In the rotating machine assembly 100 of this embodiment, the hole size (circumferential length L) of the second hole portion 32c is preferably set so that it does not come into contact with the bolt 57 under the temperature environment during use of the assembly 100. This prevents the second hole portion 32c and the bolt 57 from coming into contact with each other even if the assembly 100 is heated during use of the assembly 100.

[0053] In the rotating machine assembly 100 according to this embodiment, the absolute value of the difference between the third linear expansion coefficient α3 and the first linear expansion coefficient α1 is preferably smaller than 0.5 times the absolute value of the difference between the second linear expansion coefficient α2 and the first linear expansion coefficient α1. As a result, in comparison of the absolute value of the difference between the linear expansion coefficients, the third linear expansion coefficient α3 is closer to the first linear expansion coefficient α1 than the second linear expansion coefficient α2, thereby further reducing the possibility that the bolt 57 will be damaged due to the thermal expansion difference between the connecting ring 55 and the washer 70.

[0054] In the rotating machine assembly 100 according to this embodiment, the absolute value of the difference between the third linear expansion coefficient α3 and the first linear expansion coefficient α1 is preferably smaller than 0.1 times the absolute value of the difference between the second linear expansion coefficient α2 and the first linear expansion coefficient α1. This can further reduce the possibility of the bolt 57 being damaged due to the difference in thermal expansion between the connecting ring 55 and the washer 70.

[0055] The present disclosure is not limited to the above-described embodiments, and includes modifications to the above-described embodiments and appropriate combinations of these modifications. For example, the features of the assembly 100 according to some of the embodiments described above are not limited to the assembly 100 in the turbine 13 of the gas turbine 1, but can also be applied to assemblies in rotary machines other than the gas turbine 1 that operate in relatively high-temperature environments, such as steam turbines.

[0056] The contents described in each of the above embodiments can be understood, for example, as follows. (1) A rotating machine assembly 100 according to at least one embodiment of the present disclosure includes a first member (connecting ring 55) having a plurality of first hole portions 55a with female threads 55b formed therein, which is formed of a first metallic material having a first linear expansion coefficient α1 and extends in a circumferential direction, and a second member (connecting ring 55) that is bolted to the first member (connecting ring 55) and is provided with a plurality of second hole portions 32c that are through holes and is a different type from the first metallic material having a second linear expansion coefficient α2 that is different from the first linear expansion coefficient α1. The exhaust chamber support 32 includes a second member (exhaust chamber support 32) made of a second metal material, a plurality of bolts 57 each penetrating a second hole 32c of the second member (exhaust chamber support 32) and screwed into a first hole 55a of a first member (connecting ring 55), and a third member (washer 70) provided between a head 57h of the bolt 57 and the second member (exhaust chamber support 32) and having a plurality of third hole portions 70a as through holes, the third member (washer 70) made of a third metal material having a third linear expansion coefficient α3. The absolute value of the difference between the third linear expansion coefficient α3 and the first linear expansion coefficient α1 is smaller than the absolute value of the difference between the second linear expansion coefficient α2 and the first linear expansion coefficient α1.

[0057] If there is a difference between the second linear expansion coefficient α2 and the first linear expansion coefficient, and the second member (exhaust chamber support 32) is bolted to the first member (connecting ring 55) without the third member (washer 70), when the first member (connecting ring 55) and the second member (exhaust chamber support 32) are heated, the relative positions of the first member (connecting ring 55) and the second member (exhaust chamber support 32) in the circumferential direction are shifted due to the difference in thermal expansion between the first member (connecting ring 55) and the second member (exhaust chamber support 32). Therefore, the head 57h of the bolt 57 is pulled in the circumferential direction against the first hole portion 55a of the first member (connecting ring 55) due to friction between the seat surface 57a of the head 57h of the bolt 57 and the second member (exhaust chamber support 32), and a shear force acts on the bolt 57. Therefore, there is a risk of the bolt 57 being damaged. According to the above configuration (1), since the absolute value of the difference between the third linear expansion coefficient α3 and the first linear expansion coefficient α1 is smaller than the absolute value of the difference between the second linear expansion coefficient α2 and the first linear expansion coefficient α1, the thermal expansion difference between the first member (connecting ring 55) and the third member (washer 70) is smaller than the thermal expansion difference between the first member (connecting ring 55) and the second member (exhaust chamber support 32). As a result, even if the head 57h of the bolt 57 is pulled in the circumferential direction relative to the first hole portion 55a of the first member (connecting ring 55) due to friction between the seat surface 57a of the head 57h of the bolt 57 and the third member (washer 70) caused by the thermal expansion difference between the first member (connecting ring 55) and the third member (washer 70), the possibility of the bolt 57 being damaged can be reduced compared to the case where the second member (exhaust chamber support 32) is bolted to the first member (connecting ring 55) without the third member (washer 70).

[0058] (2) In some embodiments, in the configuration of (1) above, the first holes 55a, the second holes 32c, and the third holes 70a may be spaced apart from one another in the circumferential direction. The third member (washer 70) may be formed to extend in the circumferential direction.

[0059] According to the above configuration (2), the structure of the assembly 100 becomes rational in that the second member (exhaust chamber support 32) is pressed against the first member (connecting ring 55) extending in the circumferential direction by the third member (washer 70) to fix the second member.

[0060] (3) In some embodiments, in the configuration of (1) or (2) above, a position determining member (pin 71) may be provided for determining the relative positions of the first member (connecting ring 55), the second member (exhaust chamber support 32), and the third member (washer 70).

[0061] According to the above configuration (3), the relative positions of the first member (connecting ring 55), the second member (exhaust chamber support 32), and the third member (washer 70) are determined by the position determining member (pin 71). Therefore, even if the assembly 100 is subjected to repeated cycles of heating and cooling, causing repeated thermal expansion and contraction, the relative positions of the first member (connecting ring 55), the second member (exhaust chamber support 32), and the third member (washer 70) are unlikely to change.

[0062] (4) In some embodiments, in the configuration of (3) above, the third member (washer 70) may have an insertion hole (pin hole 70b) that is a through hole provided in a central region 70d away from both circumferential ends. The position definition member (pin 71) may be inserted into the insertion hole (pin hole 70b).

[0063] According to the above configuration (4), the maximum amount of thermal expansion in the circumferential direction of the third member (washer 70) based on the insertion hole (pin hole 70b) can be made smaller than when the insertion hole (pin hole 70b) is provided near both circumferential ends of the third member (washer 70).

[0064] (5) In some embodiments, in the configuration of (4) above, the hole size (circumferential length L) of the second hole portion 32c located at a first circumferential position among the multiple second hole portions 32c may be larger than the hole size (circumferential length L) of the second hole portion 32c located at a second position that is circumferentially closer to the position determining member (pin 71) than the first position.

[0065] According to the above configuration (5), the hole size (circumferential length L) of the second hole portion 32c located at the first position is larger than the hole size (circumferential length L) of the second hole portion 32c located at the second position which is circumferentially closer to the position determining member (pin 71) than the first position. Therefore, even when the assembly is heated, the second hole portion 32c located at the first position is less likely to come into contact with the bolt 57.

[0066] (6) In some embodiments, in any of the configurations (1) to (5) above, the size of the hole of the second hole portion 32c (circumferential length L) may be set so as not to come into contact with multiple bolts 57 under the temperature environment during use of the assembly 100.

[0067] According to the above configuration (6), even if the assembly 100 is heated during use, the second hole portion 32c and the bolt 57 will not come into contact with each other.

[0068] (7) In some embodiments, in any of the configurations (1) to (6) above, the absolute value of the difference between the third linear expansion coefficient α3 and the first linear expansion coefficient α1 may be smaller than 0.5 times the absolute value of the difference between the second linear expansion coefficient α2 and the first linear expansion coefficient α1.

[0069] According to the above configuration (7), in a comparison of the absolute values ​​of the difference between the linear expansion coefficients, the third linear expansion coefficient α3 is closer to the first linear expansion coefficient α1 than the second linear expansion coefficient α2. This further reduces the possibility that the bolt 57 will be damaged due to the difference in thermal expansion between the first member (connecting ring 55) and the third member (washer 70).

[0070] (8) In some embodiments, in any of the configurations (1) to (6) above, the absolute value of the difference between the third linear expansion coefficient α3 and the first linear expansion coefficient α1 may be smaller than 0.1 times the absolute value of the difference between the second linear expansion coefficient α2 and the first linear expansion coefficient α1.

[0071] According to the above configuration (8), it is possible to further reduce the possibility that the bolt 57 will be damaged due to the difference in thermal expansion between the first member (connection ring 55) and the third member (washer 70).

[0072] (9) In some embodiments, in any one of the configurations (1) to (6) above, the third metal material may be the same type of metal material as the first metal material.

[0073] According to the above configuration (9), the difference in thermal expansion between the first member (connecting ring 55) and the third member (washer 70) is eliminated, and the possibility of the bolt 57 being damaged can be further reduced.

[0074] (10) In some embodiments, in any of the configurations (1) to (9) above, the first member may be a flange portion (connecting ring 55) for attaching the exhaust chamber 14 to the exhaust casing 27 of the gas turbine 1, the second member may be an exhaust chamber support 32 that connects the exhaust chamber 14 and the flange portion (connecting ring 55), and the third member may be a washer 70 provided between the head 57h of the bolt 57 and the exhaust chamber support 32.

[0075] According to the above configuration (10), in the mounting structure for mounting the exhaust chamber 14 to the exhaust casing 27 of the gas turbine 1, the possibility of the bolt 57 being damaged due to the thermal expansion difference between the flange portion (connecting ring 55) and the washer 70 can be reduced. [Explanation of symbols]

[0076] 1. Gas turbine 13. Turbine 14 Exhaust chamber 21 Stator blade 21A 1st stage stator vane 22 Moving blade 22A 1st stage stator vane 24 Rotor (turbine shaft) 27 Exhaust compartment 32 Exhaust chamber support 32a Connecting flange 32c 2nd hole 32d pin hole 32P Plate-shaped part 55 Connecting Ring 55a 1st hole 55b Female thread 55c pinhole 57 Volts 57a Seat 57h head 70 Washer 70a 3rd hole 70b Pin hole 70d central area 71 pin 100 assemblies

Claims

1. a first member having a plurality of first holes with female threads formed therein, the first member being made of a first metallic material having a first linear expansion coefficient, and extending in a circumferential direction; a second member that is bolted to the first member, that is provided with a plurality of second hole portions that are through holes, and that is made of a second metal material different in type from the first metal material and that has a second linear expansion coefficient that is different from the first linear expansion coefficient; a plurality of bolts each passing through the second hole portion of the second member and screwed into the first hole portion of the first member; a third member provided between the head of the bolt and the second member, the third member having a plurality of third hole portions that are through holes, and made of a third metallic material having a third linear expansion coefficient; Equipped with an absolute value of a difference between the third linear expansion coefficient and the first linear expansion coefficient is smaller than an absolute value of a difference between the second linear expansion coefficient and the first linear expansion coefficient; Rotating machinery assemblies.

2. the first hole portions, the second hole portions, and the third hole portions are provided at intervals in the circumferential direction, The third member is formed to extend in the circumferential direction.

2. A rotary machine assembly as claimed in claim 1.

3. a position defining member for defining a relative position of the first member, the second member, and the third member; Equipped with 3. An assembly for a rotating machine according to claim 1 or 2.

4. The third member has an insertion hole which is a through hole provided in a central region away from both ends in the circumferential direction, The position defining member is inserted into the insertion hole.

4. A rotary machine assembly as claimed in claim 3.

5. Among the plurality of second hole portions, a hole size of the second hole portion located at a first position in the circumferential direction is larger than a hole size of the second hole portion located at a second position closer to the position defining member in the circumferential direction than the first position.

5. A rotary machine assembly according to claim 4.

6. a size of the second hole portion is set so as not to come into contact with the plurality of bolts under a temperature environment during use of the assembly; 3. An assembly for a rotating machine according to claim 1 or 2.

7. an absolute value of a difference between the third linear expansion coefficient and the first linear expansion coefficient is smaller than 0.5 times an absolute value of a difference between the second linear expansion coefficient and the first linear expansion coefficient; 3. An assembly for a rotating machine according to claim 1 or 2.

8. an absolute value of a difference between the third linear expansion coefficient and the first linear expansion coefficient is smaller than 0.1 times an absolute value of a difference between the second linear expansion coefficient and the first linear expansion coefficient; 3. An assembly for a rotating machine according to claim 1 or 2.

9. The third metal material is the same type of metal material as the first metal material.

3. An assembly for a rotating machine according to claim 1 or 2.

10. the first member is a flange portion for attaching an exhaust chamber to an exhaust casing of a gas turbine, the second member is an exhaust chamber support that connects the exhaust chamber and the flange portion, The third member is a washer provided between the head of the bolt and the exhaust chamber support.

3. An assembly for a rotating machine according to claim 1 or 2.

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