Turbine generator

Abstract

To provide a turbine generator which has reduced an overhang amount of a rotary shaft for supporting a turbine disk.SOLUTION: A turbine generator includes: a rotary shaft; a pair of journal bearings for supporting the rotary shaft in a rotatable manner; a generator including a generator rotor fixed to the rotary shaft between the pair of journal bearings and a stator opposed to the generator rotor; a turbine part including a turbine disk fixed to the rotary shaft on the opposite side from the generator by sandwiching one of the pair of journal bearings; a casing for storing the pair of journal bearings, the generator and the turbine part; and a seal part for sealing between a first end surface which is an end surface extending in a radial direction on the journal bearing side out of the turbine disk and an opposed surface which is the surface opposed to the first end surface in the axial direction out of the casing.SELECTED DRAWING: Figure 2

Description

[[Technical Field]]

[0001] The present disclosure relates to a turbine generator in which a turbine section and a generator are housed in a single casing. [[Background Art]]

[0002] Conventionally, there has been known a turbine provided with a seal portion for suppressing leakage of a working medium to the outside of the system. For example, the steam turbine disclosed in Patent Document 1 includes a turbine rotor, an annular ring member provided around the turbine rotor, and a seal portion configured to seal a gap formed between the turbine rotor and the ring member. [[Prior Art Literature]] [[Patent Literature]]

[0003] [[Patent Document 1]] Japanese Unexamined Patent Publication No. 2019-049218 [[Summary of the Invention]] [[Problem to be Solved by the Invention]]

[0004] In a turbine generator in which the turbine section and the generator are housed in a single casing, the turbine support portion, which is the portion of the rotating shaft that supports the turbine rotor, can be cantilevered. When the above-described seal portion is employed in such a turbine generator, it is necessary to increase the axial length of the turbine support portion. However, if the overhang amount, which is the length of the turbine support portion, becomes longer, there is a risk that the mechanical load applied to the turbine generator may increase.

[0005] An object of the present disclosure is to provide a turbine generator that reduces the overhang amount of a rotating shaft that supports a turbine disk. [[Means for Solving the Problem]]

[0006] A turbine generator according to at least one embodiment of the present disclosure includes: The axis of rotation and A pair of journal bearings that rotatably support the aforementioned rotating shaft, A generator including a generator rotor fixed to the rotating shaft between the pair of journal bearings, and a stator facing the generator rotor, A turbine section including a turbine disk fixed to the rotating shaft on the opposite side from the generator, with one of the pair of journal bearings in between, A casing for housing the pair of journal bearings, the generator, and the turbine section, the casing having an inlet for supplying a working medium to the turbine section and an outlet for discharging the working medium, A first end face of the turbine disk that extends radially on the inlet side, and a sealing portion of the casing that seals the space between the first end face and an opposing surface that is a surface in the axial direction. It is equipped with. [Effects of the Invention]

[0007] According to this disclosure, it is possible to provide a turbine generator that reduces the amount of overhang of the rotating shaft supporting the turbine disk. [Brief explanation of the drawing]

[0008] [Figure 1] This is a schematic diagram of a power generation system according to one embodiment. [Figure 2] This is a schematic cross-sectional view of a turbine generator according to one embodiment. [Figure 3A] This is a schematic diagram of the turbine section according to the first embodiment. [Figure 3B] This is a schematic diagram of the turbine section according to the second embodiment. [Figure 4] This is a schematic, partially enlarged view of the turbine section as a comparative example. [Modes for carrying out the invention]

[0009] Hereinafter, several embodiments of this disclosure will be described with reference to the attached drawings. However, the dimensions, materials, shapes, relative arrangements, etc., of the components described or shown in the drawings as embodiments are not intended to limit the scope of this disclosure, but are merely illustrative examples. For example, expressions describing relative or absolute arrangements such as "in a certain direction," "along a certain direction," "parallel," "orthogonal," "center," "concentric," or "coaxial" should not only strictly describe such arrangements, but also describe states of relative displacement with tolerances or angles or distances that allow for the same function to be achieved. For example, expressions such as "identical," "equal," and "homogeneous" that describe things being in an equal state not only describe a state of being strictly equal, but also describe a state in which there is a tolerance or a difference that is sufficient to achieve the same function. For example, expressions describing shapes such as squares or cylinders shall not only represent geometrically precise shapes such as squares or cylinders, but also shapes that include protrusions, chamfers, etc., to the extent that the same effect can be achieved. On the other hand, expressions such as "possessing," "including," or "having" one component are not exclusive expressions that exclude the existence of other components. Note that similar configurations may be given the same reference numerals and their explanations may be omitted.

[0010] <Outline of Power Generation System 1> Figure 1 is a schematic diagram showing a power generation system 1 incorporating a turbine generator 10 according to one embodiment of the present disclosure. The power generation system 1 in this example is configured to use an organic medium as a heat transfer medium, which may be, for example, R-245fa (i.e., HFC-245fa) or R1233zd(E) (i.e., HFO-1233zd(E)), which has a lower environmental impact. The power generation system 1 includes a circulation line 4 in which an evaporator 7, a turbine generator 10, and a condenser 5 are arranged in order. The evaporator 7 is configured to evaporate the heat transfer medium using heat received from a heat source. The heat source used by the evaporator 7 may be, for example, hot water. The turbine generator 10 includes a turbine section 2 and a generator 3, and the generator 3 generates electricity by driving the turbine section 2 using the gaseous heat transfer medium discharged from the evaporator 7 as a working medium. The condenser 5 is configured to condense the heat transfer medium discharged from the turbine section 2 of the turbine generator 10 using cooling water. The cooling water can be any water available for industrial use, such as seawater, lake water, or river water. The liquefied heat transfer fluid discharged from the condenser 5 is sent to the evaporator 7 by the drive of a pump 8 located in the circulation line 4.

[0011] <Overall configuration of turbine generator 10> Figure 2 is a schematic cross-sectional view of a turbine generator 10 according to one embodiment of the present disclosure. The turbine generator 10 includes a rotating shaft 15 formed from a single member. Hereinafter, the axial direction of the rotating shaft 15 will be simply referred to as the "axial direction," and one side and the other side of the axial direction will be simply referred to as "one side" and "the other side," respectively. Also, the circumferential direction and radial direction with respect to the rotating shaft 15 will be simply referred to as the "circumferential direction" and "radial direction," respectively. The inner side of the radial direction is the direction approaching the axis of the rotating shaft 15, and the outer side of the radial direction is the direction away from the axis.

[0012] The turbine generator 10 further includes a pair of journal bearings 16 that rotatably support a rotating shaft 15, and a casing 40 that supports the pair of journal bearings 16. The casing 40 of the present example is configured to partition a power generation chamber 101 and a turbine casing 102. The power generation chamber 101 is located between the pair of journal bearings 16. The turbine casing 102 is located so as to be aligned with the power generation chamber 101 with the journal bearing 16 on one side of the pair of journal bearings 16 interposed therebetween. The journal bearing 16 of the present example is a magnetic bearing.

[0013] The turbine generator 10 includes a generator 3 disposed in the power generation chamber 101 inside the casing 40. The generator 3 includes a generator rotor 32 fixed to the rotating shaft 15, and a stator 35 radially opposing the generator rotor 32. The generator rotor 32 has a rotor core and a permanent magnet supported by the rotor core, the stator 35 has a stator core 351 extending in the circumferential direction and a stator coil 352 provided on the stator core 351, and the stator core 351 is supported by the casing 40. When the generator rotor 32 rotates together with the rotating shaft 15, a current is generated in the stator coil 352, and the generator 3 can generate electric power.

[0014] Furthermore, the casing 40 of the present example is also configured to partition the power generation chamber 101 and a bearing chamber 103. The bearing chamber 103 is located so as to be aligned with the power generation chamber 101 with the journal bearing 16 on the other side interposed therebetween. In the bearing chamber 103, a thrust collar 110 fixed to the rotating shaft 15 and a pair of thrust bearings 115 axially sandwiching the thrust collar 110 are disposed. The pair of thrust bearings 115 is supported by the casing 40.

[0015] A turbine generator 10 includes a turbine section 2 arranged in a turbine casing 102. The turbine section 2 is configured to extract work from a working medium (heat medium) supplied from an inlet 41 formed in a casing 40 to rotate a rotating shaft 15, and the working medium after performing work is discharged to a condenser 5 (see Fig. 1) through an outlet 43 formed in the casing 40. In this example, the outlet 43 is located on the other side of the inlet 41, and the working medium supplied from the inlet 41 is configured to flow toward one side.

[0016] In the turbine section 2 of this example, a plurality of circumferentially arranged stationary blades and a plurality of circumferentially arranged moving blades are provided so as to be alternately arranged along the axial direction. To describe the stationary blades, the turbine section 2 is provided with a plurality of first stationary blades 91 serving as first-stage stationary blades, and a plurality of second stationary blades 92 located closer to the outlet 43 than the first stationary blades 91. A first inner ring 81 is provided inside the first stationary blades 91, and a second inner ring 82 is provided inside the second stationary blades 92. To describe the moving blades, the turbine section 2 includes a first turbine disk 21 that supports a plurality of first moving blades 211 circumferentially arranged between the first stationary blades 91 and the second stationary blades 92, and a second turbine disk 22 that supports a plurality of second moving blades 222 circumferentially arranged between the second stationary blades 92 and the outlet 43. Both the first turbine disk 21 and the second turbine disk 22 are supported by the rotating shaft 15.

[0017] Although it is not an essential component of the present disclosure, the turbine generator 10 may further include a pair of auxiliary bearings 17. The pair of auxiliary bearings 17 are arranged so as to be axially aligned with a pair of journal bearings 16 interposed therebetween. The auxiliary bearing 17 in this example is a touchdown bearing.

[0018] The positional relationship between the auxiliary bearing 17 on one side, the journal bearing 16 on the other side, and the first turbine disk 21 will be explained. The auxiliary bearing 17 is positioned in the axial direction between the journal bearing 16 and the first turbine disk 21. The auxiliary bearing 17 and the journal bearing 16 face each other in the axial direction with the first space 61 in between. Also, the auxiliary bearing 17 and the first turbine disk 21 face each other in the axial direction with the second space 62 in between.

[0019] The turbine support portion 14 is the part of the rotating shaft 15 that supports the first turbine disk 21 and the second turbine disk 22. The turbine support portion 14 protrudes to one side from the auxiliary bearing 17 and is cantilevered. More specifically, during normal operation of the turbine generator 10, the turbine support portion 14 is cantilevered by the journal bearing 16 located on one side. Furthermore, if the journal bearing 16 fails for any reason, the turbine support portion 14 is cantilevered by the auxiliary bearing 17. Therefore, the overhang amount of the rotating shaft 15, which is the axial length of the turbine support portion 14, is at least the dimension L1 shown in Figure 2.

[0020] The surface of the first turbine disk 21 facing the inlet 41 side (i.e., the other side) is the first end face 11. The surface of the casing 40 that faces the first end face 11 in the axial direction is the opposing surface 42. Both the first end face 11 and the opposing surface 42 extend in the radial direction.

[0021] The turbine generator 10 in this example includes a sealing portion 50 that seals the space between the first end face 11 and the opposing face 42. The sealing portion 50 extends in the circumferential direction. The sealing portion 50 prevents the gaseous working fluid flowing from the inlet 41 into the turbine casing 102 from leaking, for example, into the power generation chamber 101. By preventing the leakage of the working fluid necessary for doing work in the turbine casing 102, a decrease in the power generation efficiency of the turbine generator 10 is avoided.

[0022] According to the above configuration, since the seal portion 50 seals between the first end face 11 and the opposing face 42, the axial length of the seal portion 50 can be shortened, and the axial length of the turbine support portion 14 of the rotating shaft 15 can be shortened. For example, in Figure 4, which shows a turbine portion 6 as a comparative example, a seal mechanism 198 is provided between a ring body 199 fixed to the circumferential surface of the rotating shaft 15A and the casing 40A. The seal mechanism 198 is configured to seal the space between the rotating shaft 15A and the casing 40A. Because such a seal mechanism 198 is provided, the turbine support portion 14A needs to be longer in the axial direction. From this, it can be seen that by providing the seal portion 50 shown in Figure 1 instead of the seal mechanism 198, the turbine support portion 14 of the rotating shaft 15 can be shortened in the axial direction. As described above, a turbine generator 10 is realized in which the overhang amount of the rotating shaft 15 that supports the first turbine disk 21 and the second turbine disk 22 is reduced.

[0023] Furthermore, with the configuration in which the journal bearing 16 and the auxiliary bearing 17 face each other with a first space 61 in between, and the auxiliary bearing 17 and the first turbine disk 21 face each other with a second space 62 in between, at least in the axial range from the journal bearing 16 to the first turbine disk 21, there are no sealing means provided on the circumferential surface of the rotating shaft 15 except for the auxiliary bearing 17. In other words, the rotating shaft 15 is not provided with sealing means such as the sealing mechanism 198 (see Figure 4). This makes it possible to reduce the amount of overhang of the rotating shaft 15.

[0024] Furthermore, in some embodiments, the seal portion 50 is a labyrinth seal (see Figures 3A and 3B). The labyrinth seal includes a recess provided on either the opposing surface 42 of the casing 40 or the first end surface 11 of the first turbine disk 21, and a protrusion provided on the other. Both the recess and the protrusion extend in the circumferential direction, and the protrusion enters the recess. With the above configuration, the labyrinth seal can suppress leakage of the working medium.

[0025] <Additional components of the turbine generator 10> Figures 3A and 3B schematically illustrate the turbine section 2A(2) according to the first embodiment and the turbine section 2B(2) according to the second embodiment, respectively.

[0026] As shown in Figures 3A and 3B, the first turbine disk 21, which is a component of the turbine sections 2A and 2B(2), includes an annular portion 219 fixed to the rotating shaft 15 and a radially extended portion 27 extending radially outward from the outer peripheral surface 214 of the annular portion 219. The first end face 11 described above is formed on the radially extended portion 27. A balance hole 25 is also formed on the radially extended portion 27. The balance hole 25 is a hole that is open in the axial direction. By allowing the working fluid to pass through the balance hole 25, the pressure difference between the space 66 between the first stator blade 91 and the first rotor blade 211 and the space 67 between the first rotor blade 211 and the second stator blade 92 can be reduced.

[0027] The second turbine disk 22 has the same configuration as the first turbine disk 21. Specifically, the second turbine disk 22 includes an annular portion 229 fixed to the rotating shaft 15 and a radially extending portion 28 extending radially from the outer circumferential surface 224 of the annular portion 229, and a balance hole 24 is formed in the radially extending portion 28. The outer circumferential surface 224 of the second turbine disk 22 is positioned at the same radial position as the outer circumferential surface 214 of the first turbine disk 21, and the outer circumferential surfaces 214 and 224 are radially opposite to the second inner ring 82 provided inside the second stationary vane 92. A sealing mechanism 55 is also positioned between the second inner ring 82 and the outer circumferential surfaces 214 and 224. The balance holes 24 and 25 are positioned at the same radial position relative to each other.

[0028] As shown in Figures 3A and 3B, the seal portions 50A and 50B (50) are located radially outward from the outer circumferential surface 214 of the first turbine disk 21. With this configuration, the seal portions 50A and 50B can reduce the pressure in the space radially inward from the seal portions 50A and 50B. This reduces the pressure difference between the first space 61, which is the space on the inlet 41 side of the annular portion 219, and the space on the outlet 43 side. Specifically, the pressure difference between the first space 61 and the space on one side of the second turbine disk 22 can be reduced. This reduces the thrust force, which is an axial force acting on the annular portion 219. Therefore, the mechanical load on the thrust bearing 115 can be reduced.

[0029] Furthermore, the thrust forces acting on the first turbine disk 21 and the second turbine disk 22 are offset by the reaction forces acting on the thrust collar 110 from the pair of thrust bearings 18 (see Figure 1) described above.

[0030] Furthermore, as shown in Figures 3A and 3B, the seal portions 50A and 50B (50) are located radially inward from the balance hole 25 of the first turbine disk 21. With this configuration, radially outward from the balance hole 25, the relationship between the pressure of the working medium between the space 66 on the inlet 41 side and the space 67 on the outlet 43 side of the first turbine disk 21 can be maintained at a desired level. Specifically, in the example shown in the figures, the pressure in space 66 can be maintained to be greater than the pressure in space 67. As a result, compared to the case where the seal portion 50 is located radially outward from the balance hole 25 of the first turbine disk 21, the switching of the direction of the thrust force acting on the first turbine disk 21 is suppressed, and in the example shown in Figures 3A and 3B, the direction of the thrust force acting on the first turbine disk 21 is maintained to one side in the axial direction (arrow F1). This makes it possible to avoid instability in the control of the journal bearing 16 caused by frequent switching of the direction of the thrust force. Furthermore, if the seal portion 50 is located radially outward from the balance hole 25 of the first turbine disk 21, depending on the turbine load, the working fluid may flow back from space 67 to space 66, potentially causing a change in the direction of the thrust force. Furthermore, since the seal portions 50A and 50B are located radially inward from the balance hole 25, the seal portions 50A and 50B can be brought closer to the rotating shaft 15. This shortens the circumferential length (in other words, the annular area) of the seal portions 50A and 50B, suppressing the amount of leakage of the working fluid from the seal portions 50A and 50B, thereby maintaining the performance of the turbine portions 2A and 2B(2).

[0031] Furthermore, by arranging the seal portions 50A and 50B to be located inside the balance hole 25 and radially outside the outer peripheral surface 214, it is possible to reduce the thrust force acting on the first turbine disk 21 while maintaining the performance of the turbine portions 2A and 2B(2).

[0032] Furthermore, as shown in Figure 3A, in some embodiments, the entire seal portion 50A is located on the outer circumferential surface 214 side of the radial midpoint between the inner end 251 of the balance hole 25 and the outer circumferential surface 214 of the annular portion 219. In Figure 3A, this midpoint is on the dashed line M1 (the same applies to Figure 3B). With the above configuration, the seal portion 50A can be brought closer to the rotating shaft 15, so the circumferential length of the seal portion 50A can be further shortened. The amount of leakage of the working medium from the seal portion 50A can be further reduced, and the performance of the turbine portion 2A can be maintained.

[0033] Furthermore, as shown in Figure 3B, in some embodiments, the entire seal portion 50B is located closer to the balance hole 25 than the intermediate position described above. With this configuration, the seal portion 50B can be moved radially away from the outer circumferential surface 214 of the annular portion 219, thereby further reducing the thrust force acting on the first turbine disk 21.

[0034] <Other variations> The turbine generator 10 may comprise a pair of turbine sections 2. In this case, turbine casings 102 are formed on one and the other axial side of the power generation chamber 101, and a turbine section 2 is arranged in each turbine casing 102. The turbine section 2 may further comprise stationary blades and rotor blades between the second rotor blades 222 and the outlet 43, or a single-stage configuration without the second stationary blades 92 and the second rotor blades 222 may be adopted for the turbine section 2. Furthermore, this disclosure is not limited to the working fluid flowing from the other axial side to the one axial side in the turbine casing 102. For example, the outlet 43 and the inlet 41 may be arranged sequentially from the other axial side to the one axial side. In this case, the turbine section 2, having obtained work from the working fluid flowing axially toward the other side in the turbine casing 102, is configured to rotate the rotating shaft 15.

[0035] <Summary> The contents described in some of the embodiments above can be understood, for example, as follows:

[0036] 1) A turbine generator (10) according to at least one embodiment of the present disclosure is Rotation axis (15) and, A pair of journal bearings (16) that rotatably support the aforementioned rotating shaft, A generator (3) includes a generator rotor (32) fixed to the rotating shaft between the pair of journal bearings, and a stator (35) facing the generator rotor, A turbine section (2) including a turbine disk (first turbine disk 21) fixed to the rotating shaft on the opposite side from the generator, with one of the pair of journal bearings in between, A casing for housing the pair of journal bearings, the generator, and the turbine section, the casing (40) having an inlet (41) for supplying a working medium to the turbine section and an outlet (43) for discharging the working medium, The turbine disk has a first end face (11) that extends radially on the inlet side, and the casing has a sealing portion (50) that seals the space between the first end face and the opposing surface (42) that is a surface in the axial direction. It is equipped with.

[0037] According to the configuration described in 1) above, since the seal portion seals between the first end face and the opposing face, the length of the seal portion in the axial direction can be shortened, and the length of the part of the rotating shaft that supports the turbine rotor can be shortened. Therefore, a turbine generator with a reduced overhang of the rotating shaft that supports the turbine disk can be realized.

[0038] 2) In some embodiments, the turbine generator is as described in 1) above, The turbine disk includes an annular portion (219) fixed to the rotating shaft and a radially extending portion (27) that extends radially outward from the outer peripheral surface (214) of the annular portion and has a first end face. The sealing portion is located radially outward from the outer circumferential surface of the annular portion.

[0039] According to the configuration described in 2) above, it becomes possible to reduce the pressure in the space radially inside the seal portion, thereby reducing the pressure difference between the space on the inlet side of the annular portion (first space 61) and the space on the outlet side of the turbine disk. This reduces the thrust force acting on the annular portion. Furthermore, in embodiments in which a thrust bearing (115) is provided on the rotating shaft, the mechanical load on the thrust bearing can be reduced.

[0040] 3) In some embodiments, the turbine generator is as described in 1) or 2) above, The turbine disk has a balance hole (25) that penetrates in the axial direction. The sealing portion is located radially inward from the balance hole.

[0041] According to the configuration described in 3) above, the relative pressure relationship between the space on the inlet side (66) and the space on the outlet side (67) of the turbine disk, radially outside the balance hole, can be maintained in the desired relationship. As a result, the switching of the direction of the thrust force acting on the turbine disk is suppressed compared to the case where the seal portion is located radially outside the balance hole, and instability in the control of the journal bearing can be avoided. Note that when the seal portion is located radially outside the balance hole, there is a risk that the working fluid will flow from the outlet side space to the inlet side space, causing the thrust force to switch. Furthermore, since the seal is located radially inward from the balance hole, the seal can be brought closer to the axis of rotation. This shortens the circumferential length (in other words, the annular area) of the seal, suppressing leakage of the working fluid from the seal, thereby maintaining the performance of the turbine.

[0042] 4) In some embodiments, the turbine generator is as described in 1) above, The turbine disk includes an annular portion (219) fixed to the rotating shaft and a radially extending portion (27) that extends radially outward from the outer peripheral surface (214) of the annular portion and has a first end face. A balance hole (25) is formed in the radially extending portion, which penetrates in the axial direction. The sealing portion is located radially inward from the balance hole and radially outward from the outer circumferential surface of the annular portion.

[0043] According to the configuration described in 4) above, it is possible to reduce the thrust force acting on the turbine disk while maintaining the performance of the turbine section.

[0044] 5) In some embodiments, the turbine generator is as described in 4) above, The sealing portion is located on the outer circumferential surface side of the midpoint in the radial direction between the inner end (251) of the balance hole and the outer circumferential surface of the annular portion.

[0045] According to the configuration described in 5) above, the seal portion can be brought closer to the rotating shaft, thus further shortening the circumferential length of the seal portion. This further reduces the amount of leakage of the working fluid from the seal portion, and maintains the performance of the turbine portion.

[0046] 6) In some embodiments, the turbine generator is as described in 4) above, The sealing portion is located on the balance hole side of the midpoint between the inner end (251) of the balance hole and the outer surface of the annular portion in the radial direction.

[0047] According to the configuration in 6) above, the seal portion can be separated radially from the outer surface of the annular portion, thereby further reducing the thrust force acting on the turbine disk.

[0048] 7) In some embodiments, a turbine generator according to any one of 1) to 6) above, The aforementioned sealing portion is a labyrinth seal.

[0049] According to the configuration described in 7) above, the labyrinth seal can suppress leakage of the working medium.

[0050] 8) In some embodiments, a turbine generator according to any one of 1) to 7) above, The system further comprises a pair of auxiliary bearings (17) that support the aforementioned rotating shaft, One of the pair of auxiliary bearings is positioned in an axial location between the journal bearing and the seal portion. One journal bearing and the other auxiliary bearing face each other in the axial direction with the first space (61) in between. On the other hand, the auxiliary bearing and the turbine disk face each other in the axial direction with the second space (62) in between.

[0051] According to the configuration described in 8) above, since no sealing means are provided on the circumferential surface of the rotating shaft except for the auxiliary bearing 17 in the axial range from the journal bearing to the turbine disk, the amount of overhang of the rotating shaft supporting the turbine disk can be reduced. [Explanation of symbols]

[0052] 1: Power generation system 2: Turbine section 3: Generator 4: Circulation line 5: Condenser 6: Turbine section 7: Evaporator 8: Pump 10: Turbine generator 11: First end surface 14,14A: Turbine support section 15,15A: Rotation axis 16: Journal bearing 17: Auxiliary bearings 18: Thrust bearing 19: Refrigerant flow path 21: First turbine disk 22: Second Turbine Disc 24,25: Balance Hole 27,28: Radial extension part 32: Generator Rotor 35: Status 40,40A: Casing 41:Inlet 42: Opposing surface 43: Outlet 50: Seal part 55: Seal mechanism 61: 1st space 62:Second space 63:Third space 66,67 :Space 81: First Inner Ring 82: Second Inner Ring 91: First Static Wing 92: Second Static Wing 101: Power Generation Room 102: Turbine casing 103: Bearing chamber 110: Thrust Color 115: Thrust bearing 198: Seal mechanism 199: Ring body 211: 1st rotor blade 214,224: Outer surface 219,229: Ring section 222: 2nd rotor blade 251 :Inner edge 351: Stator Core 352: Stator coil F1: Arrow L1: Dimensions M1: Two-dot chain line

Claims

1. The axis of rotation and A pair of journal bearings that rotatably support the aforementioned rotating shaft, A generator including a generator rotor fixed to the rotating shaft between the pair of journal bearings, and a stator facing the generator rotor, A turbine section including a turbine disk fixed to the rotating shaft on the opposite side from the generator, with one of the pair of journal bearings in between, A casing for housing the pair of journal bearings, the generator, and the turbine section, the casing having an inlet for supplying a working medium to the turbine section and an outlet for discharging the working medium, A first end face of the turbine disk that extends radially on the inlet side, and a sealing portion of the casing that seals the space between the first end face and an opposing surface that is a surface in the axial direction. A turbine generator equipped with a turbine generator.

2. The turbine disk includes an annular portion fixed to the rotating shaft and a radially extending portion that extends radially outward from the outer circumferential surface of the annular portion and has a first end face. The sealing portion is located radially outward from the outer circumferential surface of the annular portion. The turbine generator according to claim 1.

3. The turbine disk has a balance hole that penetrates in the axial direction. The sealing portion is located radially inward from the balance hole. The turbine generator according to claim 1 or 2.

4. The turbine disk includes an annular portion fixed to the rotating shaft and a radially extending portion that extends radially outward from the outer circumferential surface of the annular portion and has a first end face. A balance hole is formed in the radially extending portion, which penetrates in the axial direction. The sealing portion is located radially inward from the balance hole and radially outward from the outer surface of the annular portion. The turbine generator according to claim 1.

5. The sealing portion is located on the outer circumferential surface side of the midpoint between the inner end of the balance hole and the outer circumferential surface of the annular portion in the radial direction. The turbine generator according to claim 4.

6. The sealing portion is located on the balance hole side of the midpoint between the inner end of the balance hole and the outer surface of the annular portion in the radial direction. The turbine generator according to claim 4.

7. The aforementioned sealing portion is a labyrinth seal. The turbine generator according to claim 1 or 2.

8. The system further comprises a pair of auxiliary bearings that support the aforementioned rotating shaft, One of the pair of auxiliary bearings is positioned in an axial location between the journal bearing and the seal portion. One of the journal bearings and the other auxiliary bearing face each other in the axial direction with the first space in between. On the other hand, the auxiliary bearing and the turbine disk face each other in the axial direction with a second space in between. The turbine generator according to claim 1 or 2.

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