Rotating electric machine system and hybrid power system equipped with the same

Abstract

To provide a rotary electric machine system that can detect accurate rotational parameters.SOLUTION: In a rotary electric machine system, a rotary shaft 40 of a rotary electric machine has a hollow cylindrical outer shaft 44 and an inner shaft 42 that is inserted in a hollow interior of the outer shaft. The inner shaft has a protruding tip 46 that is exposed from the outer shaft. A rotational parameter detector, a holding member, and a restraining member 60 are provided on the protruding tip. The holding member supports the rotational parameter detector on the protruding tip. The restraining member restrains the inner shaft to the outer shaft.SELECTED DRAWING: Figure 5

Description

[Technical Field]

[0001] The present invention relates to a rotating electric machine system, and also to a hybrid power system in which a rotating electric machine system and an internal combustion engine are integrally configured. [Background technology]

[0002] A combined power system includes a rotating electric machine system and an internal combustion engine. As described in Patent Documents 1 to 4, in a combined power system, the rotating shaft of the rotating electric machine system and the output shaft of the internal combustion engine are connected coaxially. Therefore, the rotating shaft and the output shaft rotate integrally. As the rotating shaft rotates integrally with the output shaft, the rotating electric machine system functions, for example, as a generator. The rotating shaft is rotatably supported via bearings in a rotating electric machine housing that houses the rotating electric machine.

[0003] The rotating electric machine system also includes a rotation parameter detector for detecting rotation parameters such as the rotation speed, rotation angle, or number of rotations of the rotating shaft. The rotation parameter detector is disposed, for example, around the rotating shaft. In this case, the rotation parameters can be accurately detected. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Laid-Open No. 2002-147250 [Patent Document 2] Japanese Patent Application Laid-Open No. 2005-106029 [Patent Document 3] Japanese Patent Application Laid-Open No. 2004-232532 [Patent Document 4] Japanese Patent Application Laid-Open No. 2003-343204 Summary of the Invention [Problem to be solved by the invention]

[0005] There is a demand for rotating electrical machines that can generate more power while reducing their size. To meet this demand, it is necessary to rotate the rotating shaft at high speed. However, this increases the vibrations generated in the rotating shaft. This makes it difficult to accurately detect rotation parameters and reduces the durability of the rotation parameter detector.

[0006] The present invention aims to solve the above-mentioned problems. [Means for solving the problem]

[0007] According to one embodiment of the present invention, there is provided a rotating electric machine system having a rotating electric machine and a rotating electric machine housing that rotatably supports a rotating shaft of the rotating electric machine, The rotating shaft has a hollow cylindrical outer shaft and an inner shaft that is removably inserted into the hollow interior of the outer shaft, the outer shaft has a first outer shaft end portion and a second outer shaft end portion located opposite to each other in the axial direction of the rotating shaft, the inner shaft has a first inner shaft end portion and a second inner shaft end portion positioned opposite to each other in the axial direction, the first inner shaft end of the inner shaft has a protruding tip exposed from the first outer shaft end of the outer shaft, a rotation parameter detector provided at the protruding tip to detect a rotation parameter of the rotating shaft; a holding member provided at the protruding tip to support the rotation parameter detector at the protruding tip; a restraining member provided at the protruding tip end and configured to restrain the inner shaft to the outer shaft; A rotating electrical machine system is provided.

[0008] According to another embodiment of the present invention, there is provided a hybrid power system including the above rotating electric machine system. [Effects of the Invention]

[0009] According to the present invention, the inner shaft is restrained to the outer shaft by the restraining member, which makes it difficult for the inner shaft to become eccentric with respect to the outer shaft, thereby making it possible to suppress vibration of the rotating shaft even when the rotating shaft is rotated at high speed. [Brief explanation of the drawings]

[0010] [Figure 1] FIG. 1 is a schematic overall perspective view of a combined power system according to an embodiment of the present invention. [Figure 2] FIG. 2 is a schematic overall perspective view of the rotating electrical machine system according to the embodiment of the present invention. [Figure 3] FIG. 3 is a schematic cross-sectional side view of the rotating electrical machine system. [Figure 4] FIG. 4 is an enlarged view of the main part of FIG. [Figure 5] FIG. 5 is an enlarged view of the main part of FIG. [Figure 6] FIG. 6 is an enlarged view of a main part of FIG. 3 at a location different from that of FIG. [Figure 7] FIG. 7 is a schematic diagram of a current converter provided in a housing of a rotating electrical machine. [Figure 8] FIG. 8 is a schematic perspective view of a second sub-housing that constitutes the rotary electric machine housing and an inner housing in the engine housing. [Figure 9] FIG. 9 is a schematic cross-sectional side view of a gas turbine engine that constitutes a combined power system. [Figure 10] FIG. 10 is an enlarged view of the main part of FIG. DETAILED DESCRIPTION OF THE INVENTION

[0011] In the following description, "left," "right," "bottom," and "top" refer to the left, right, bottom, and top directions, respectively, in particular in Figures 3 to 6, 9, and 10. However, these directions are merely used for convenience to simplify the description and make it easier to understand. In other words, the directions described in the specification are not necessarily the directions when the combined power system is actually used.

[0012] 1 is a schematic overall perspective view of a combined power system 400 according to this embodiment. The combined power system 400 includes a rotating electric machine system 10 and a gas turbine engine 200 as an internal combustion engine. An axis passing through the diameter center of the rotating electric machine system 10 and extending along the longitudinal direction (axial direction) coincides with an axis passing through the diameter center of the gas turbine engine 200 and extending along the longitudinal direction (axial direction). In other words, the rotating electric machine system 10 and the gas turbine engine 200 are arranged on the same axis.

[0013] Hereinafter, the left end in the axial direction of each of the rotating electric machine system 10 and the gas turbine engine 200 may be referred to as a first end. Similarly, the right end in the axial direction of each of the rotating electric machine system 10 and the gas turbine engine 200 may be referred to as a second end. That is, in the rotating electric machine system 10, the left end remote from the gas turbine engine 200 is the first end. In the rotating electric machine system 10, the right end close to the gas turbine engine 200 is the second end. Also, in the gas turbine engine 200, the left end close to the rotating electric machine system 10 is the first end. In the gas turbine engine 200, the right end remote from the rotating electric machine system 10 is the second end. According to this definition, in the illustrated example, the gas turbine engine 200 is disposed at the second end of the rotating electric machine system 10. The rotating electric machine system 10 is disposed at the first end of the gas turbine engine 200.

[0014] The combined power system 400 is used as a propulsion power source in, for example, an air vehicle, a ship, or an automobile. Suitable examples of the air vehicle include a drone or a multicopters. When mounted on an air vehicle, the combined power system 400 serves as a power drive source that rotates a propeller or a ducted fan, for example. When mounted on a ship, the combined power system 400 serves as a rotational force generating device for a screw. When mounted on an automobile, the combined power system 400 serves as a power drive source that rotates a motor.

[0015] The combined power system 400 can also be used as a power source for auxiliary power supplies in aircraft, ships, buildings, etc. In addition, the combined power system 400 can also be used as a gas turbine power generation facility.

[0016] As will be described later, the gas turbine engine 200 is an internal combustion engine and a gas supply device that supplies compressed air.

[0017] First, the rotating electric machine system 10 will be described. Fig. 2 is a schematic overall perspective view of the rotating electric machine system 10. Fig. 3 is a schematic side cross-sectional view of the rotating electric machine system 10. The rotating electric machine system 10 includes a rotating electric machine 12 (e.g., a generator) and a rotating electric machine housing 14 that houses the rotating electric machine 12.

[0018] The rotating electrical machine housing 14 has a main housing 16, a first sub-housing 18, and a second sub-housing 20. The main housing 16 has a generally cylindrical shape, and both a first end and a second end are open ends. The first sub-housing 18 is connected to the first end (left open end) of the main housing 16. The second sub-housing 20 is connected to the second end (right open end) of the main housing 16. As a result, the first and second ends of the main housing 16 are closed.

[0019] The main housing 16 has thick side walls extending in the left-right direction. A storage chamber 22 is formed inside the side walls. Most of the rotating electrical machine 12 is housed in the storage chamber 22.

[0020] A spiral cooling jacket 24 is formed inside the side wall of the main housing 16. A cooling medium flows through the cooling jacket 24. A specific example of the cooling medium is cooling water. In this case, the cooling jacket 24 is a water jacket.

[0021] A first casing 26 and a second casing 28 are provided on the outer surface (outer wall) of the side wall of the main housing 16 near the edge of the first end. The first casing 26 and the second casing 28 are part of the main housing 16. In other words, the first casing 26 and the second casing 28 are provided integrally with the main housing 16. As will be described later, the first casing 26 is a terminal casing. The second casing 28 is a meter casing.

[0022] A holding member that holds a rotation parameter detector is connected to the first sub-housing 18. In this embodiment, a resolver 132 is exemplified as the rotation parameter detector. Therefore, hereinafter, the holding member for the rotation parameter detector will be referred to as a "resolver holder 30." As will be described later, a cap cover 32 is connected to the resolver holder 30 via screws.

[0023] The rotating electric machine 12 includes a rotor 34 and a stator 36 that surrounds the outer periphery of the rotor 34 .

[0024] The rotor 34 includes a rotating shaft 40. The rotating shaft 40 has an inner shaft 42 and a hollow cylindrical outer shaft 44. Both ends of the outer shaft 44 are open ends. That is, the outer shaft 44 has a left open end 441 (see FIG. 4) as a first outer shaft end and a right open end 442 (see FIG. 6) as a second outer shaft end. The inner shaft 42 is removably inserted into the outer shaft 44.

[0025] The inner shaft 42 is longer than the outer shaft 44. The inner shaft 42 has a cylindrical portion 421, a left end portion 422 (see FIG. 4) as a first inner shaft end portion, and a right end portion 423 (see FIG. 6) as a second inner shaft end portion.

[0026] The right end portion 423 is connected to the right side of the cylindrical portion 421. Therefore, the right end portion 423 is the other end (second end) of the inner shaft 42 that is close to the gas turbine engine 200. The diameter of the right end portion 423 is larger than the diameter of the cylindrical portion 421. In the illustrated example, the right end portion 423 of the inner shaft 42 and the right open end 442 of the outer shaft 44 are flush with each other. However, the right end portion 423 may be located slightly closer to the second end from the right open end 442.

[0027] The left end portion 422 is connected to the left side of the cylindrical portion 421. Therefore, the left end portion 422 is one end (first end) of the inner shaft 42 that is away from the gas turbine engine 200. As shown in Fig. 4, the left end portion 422 has a protruding tip 46, a constant diameter portion 471, and an expanded diameter portion 472. The protruding tip portion 46, the constant diameter portion 471, and the expanded diameter portion 472 are arranged in this order from the direction away from the cylindrical portion 421 to the direction approaching it.

[0028] The protruding tip 46 is a portion of the left end 422 that is exposed from the left open end 441 of the outer shaft 44. The protruding tip 46 has a small diameter portion 48, a flange portion 50, a stopper portion 52, and a large diameter portion 54. The outer diameters of the small diameter portion 48, the flange portion 50, the stopper portion 52, and the large diameter portion 54 increase in this order.

[0029] The diameter (outer diameter) of the large diameter portion 54 is the largest among all portions of the inner shaft 42, and is larger than the inner diameter of the outer shaft 44. Therefore, the right end of the large diameter portion 54 abuts against the edge of the left open end 441 of the outer shaft 44. Therefore, the portion of the inner shaft 42 to the left of the large diameter portion 54 is not inserted into the outer shaft 44. Therefore, the protruding tip 46 remains exposed from the left open end 441 of the outer shaft 44.

[0030] At the protruding tip 46, a first external thread 551 is formed on the side peripheral wall (outer surface) of the small diameter portion 48. At the protruding tip 46, a second external thread 552 (first thread) is formed on the side peripheral wall (outer surface) of the large diameter portion 54. The second external thread 552 is formed between the left open end 441 of the outer shaft 44 and the resolver rotor 56 in the axial direction of the rotating shaft 40.

[0031] The constant diameter portion 471 and the expanded diameter portion 472 are inserted into the outer shaft 44. The constant diameter portion 471 protrudes from the right end of the large diameter portion 54. The diameter of the constant diameter portion 471 is smaller than the diameter of the large diameter portion 54 and larger than the diameter of the cylindrical portion 421. The difference between the diameter of the constant diameter portion 471 and the inner diameter of the left open end 441 of the outer shaft 44 is approximately 20 μm. For example, the diameter of the constant diameter portion 471 is approximately 20 μm smaller than the inner diameter of the left open end 441 of the outer shaft 44. Therefore, the constant diameter portion 471, which is a part of the inner shaft 42, and the left open end 441 of the outer shaft 44 are spigot-fitted. That is, as shown in FIGS. 4 and 5 , a first spigot-fitting portion 571 is formed between the constant diameter portion 471 and the left open end 441. When the diameter of the constant diameter portion 471 is approximately 20 μm larger than the inner diameter of the left open end 441 of the outer shaft 44, the constant diameter portion 471 is lightly press-fitted into the left open end 441. In this way, the spigot fitting includes light press-fitting.

[0032] Expanded diameter portion 472 is a portion whose diameter increases in a tapered manner as it moves away from cylindrical portion 421. The left end of expanded diameter portion 472 is continuous with the right end of constant diameter portion 471. The diameter of the left end of expanded diameter portion 472 is equal to the diameter of the right end of constant diameter portion 471. The right end of expanded diameter portion 472 is continuous with the left end of cylindrical portion 421. The diameter of the right end of expanded diameter portion 472 is equal to the diameter of the left end of cylindrical portion 421.

[0033] A resolver rotor 56 is attached to the flange 50. A small cap nut 58 is screwed onto the first external thread 551. The right end of the resolver rotor 56 abuts against the stopper portion 52. Therefore, the resolver rotor 56 stops. In this state, the left end of the resolver rotor 56 is pressed by the small cap nut 58. As a result, the resolver rotor 56 is axially held between the small cap nut 58 and the stopper portion 52, and the resolver rotor 56 is positioned and fixed to the flange 50.

[0034] The second external thread 552 is covered by the large cap nut 60. Here, an internal thread 611, which is a second thread, is formed in part of the inner circumferential wall (inner surface) of the large cap nut 60. The internal thread 611 reaches the left end of the inner circumferential wall of the large cap nut 60. This internal thread 611 is threadedly engaged with the second external thread 552. As a result of this engagement, a force is applied from the large cap nut 60 to the inner shaft 42, pulling the inner shaft 42 to the right. This force causes the right end face of the large diameter portion 54 to abut against the edge face of the left open end 441 of the outer shaft 44, thereby positioning the inner shaft 42.

[0035] The large cap nut 60 does not have an internal thread 611 formed on the inner peripheral wall near the right open end. Therefore, an accommodation hole 612 is formed at the right end of the large cap nut 60, between the right open end and the right end of the internal thread 611.

[0036] When the inner thread 611 is threaded onto the second outer thread 552, the left opening end 441 of the outer shaft 44 is inserted into the accommodating hole 612. The difference between the inner diameter of the accommodating hole 612 and the outer diameter of the left opening end 441 is approximately 20 μm. For example, the outer diameter of the left opening end 441 is approximately 20 μm smaller than the inner diameter of the accommodating hole 612. Therefore, the inner circumferential wall of the accommodating hole 612 and the left opening end 441, which is a part of the outer shaft 44, are spigot-fitted. As a result, as shown in FIGS. 4 and 5 , a second spigot-fitting portion 572 is formed between the large cap nut 60 and the left opening end 441. The left end portion 422 of the inner shaft 42 is constrained to the left opening end 441 of the outer shaft 44 by the second spigot-fitting portion 572. In this way, the large cap nut 60 is a constraining member that constrains the inner shaft 42 to the outer shaft 44.

[0037] When the outer diameter of the left opening end 441 is approximately 20 μm larger than the inner diameter of the receiving hole 612, the left opening end 441 is lightly press-fitted into the receiving hole 612. In this way, this spigot fitting also includes light press-fitting.

[0038] As can be understood from the above, in this embodiment, the constant diameter portion 471 (part of the left end portion 422) of the inner shaft 42 and the left open end 441 of the outer shaft 44 are spigot-fitted. Also, the inner circumferential wall of the accommodation hole 612 of the large cap nut 60 (restraint member) and the left open end 441 of the outer shaft 44 are spigot-fitted. As described above, spigot-fitting includes light press-fitting.

[0039] The first outer thread 551 and the second outer thread 552 are so-called reverse threads. Therefore, the small cap nut 58 and the large cap nut 60 are rotated counterclockwise when screwed together. After screwing together, it is preferable to deform part of the threads of the small cap nut 58 and the large cap nut 60. This prevents the small cap nut 58 and the large cap nut 60 from loosening.

[0040] As shown in Fig. 6, a connecting hole 62 is formed in the right end 423, which is the second end, of the inner shaft 42. The connecting hole 62 extends toward the left end 422, which is the first end. An internal thread 64 is formed in the inner circumferential wall of the connecting hole 62. The left end of the output shaft 204 is inserted into the connecting hole 62. The left end of the output shaft 204 is coupled to the inner shaft 42 by being threaded into the internal thread 64. The output shaft 204 holds a compressor wheel 222 and a turbine wheel 224 (see Fig. 9).

[0041] A first internal spline 66 is formed on the outer peripheral wall of the right open end 442 of the outer shaft 44. The first internal spline 66 extends along the axial direction of the rotary electric machine system 10 (left-right direction).

[0042] As shown in Figure 3, the outer diameter of the outer shaft 44 is greatest at approximately the middle part in the longitudinal direction. In this large-diameter middle part, multiple permanent magnets 72 are held via magnet holders 70. The polarities of two adjacent permanent magnets 72 face outward. As the rotating shaft 40 rotates, the permanent magnets 72 move around the rotation center of the rotating shaft 40 on the circumference of a predetermined imaginary circle.

[0043] The left end (first end) of the rotating shaft 40 is rotatably supported by the first sub-housing 18 via a first bearing 74. As shown in FIG. 3 , the first bearing 74 is inserted between the outer shaft 44 and the first sub-housing 18. Specifically, the first sub-housing 18 has a cylindrical protrusion 76 that protrudes toward the main housing 16. A first insertion hole 78 is formed in the cylindrical protrusion 76. A first bearing holder 80 that holds the first bearing 74 is inserted into the first insertion hole 78. Therefore, the first bearing 74 is disposed in the first insertion hole 78.

[0044] The first insertion hole 78 extends in the left-right direction. The left end of the first insertion hole 78 is farther from the output shaft 204 than the right end of the first insertion hole 78. Hereinafter, the left end of the first insertion hole 78 will also be referred to as the "first distal end 781." On the other hand, the right end of the first insertion hole 78 is closer to the output shaft 204 than the left end of the first insertion hole 78 (first distal end 781). Hereinafter, the right end of the first insertion hole 78 will also be referred to as the "first proximal end 782."

[0045] A first outer stopper 81 located at a first distal end 781 and a first inner stopper 82 located at a first proximal end 782 are attached to the small-diameter left end of the outer shaft 44. The first bearing 74 is sandwiched between the first outer stopper 81 and the first inner stopper 82. The first bearing 74 is positioned and fixed based on this sandwiching. A clearance is formed between the first outer stopper 81 and the cylindrical protrusion 76.

[0046] The tip of the left end of the rotating shaft 40 is passed through the inner hole of the first bearing 74 and then passes through the first insertion hole 78. The tip of the left end of the rotating shaft 40 is exposed outside the cylindrical protrusion 76 (hollow recess 118). Furthermore, at the left end of the rotating shaft 40, the protruding tip 46 of the inner shaft 42 is exposed from the left open end 441 of the outer shaft 44. As described above, the protruding tip 46 includes the small diameter portion 48, the flange portion 50, the stopper portion 52, and the large diameter portion 54 (see FIG. 4).

[0047] The right end (second end) of the rotating shaft 40 is rotatably supported by the second sub-housing 20 via a second bearing 84. As shown in Fig. 6, the second bearing 84 is inserted between the outer shaft 44 and the second sub-housing 20, which has a substantially circular plate shape.

[0048] The second sub-housing 20 is connected to the main housing 16 via bolts (not shown). The center of the second sub-housing 20 is a thick-walled cylindrical portion. A second insertion hole 86 is formed in the cylindrical portion. The second insertion hole 86 extends in the left-right direction. The left end of the second insertion hole 86 is farther from the output shaft 204 than the right end of the second insertion hole 86. Hereinafter, the left end of the second insertion hole 86 will also be referred to as the "second distal end 861." On the other hand, the right end of the second insertion hole 86 is closer to the output shaft 204 than the left end (second distal end 861) of the second insertion hole 86. Hereinafter, the right end of the second insertion hole 86 will also be referred to as the "second proximal end 862."

[0049] A second bearing holder 88 holding a second bearing 84 is inserted into the second insertion hole 86. Thus, the second bearing 84 is disposed in the second insertion hole 86. The second bearing 84 is sandwiched between a second inner stopper 90 located at the second distal end 861 and a second outer stopper 92 located at the second proximal end 862. Based on this sandwiching, the second bearing 84 is positioned and fixed.

[0050] At the second distal end 861, a clearance is formed between the second inner stopper 90 and the second bearing holder 88. This clearance is a first sub-branch passage 941. Lubricating oil is supplied to the first bearing 74 and the second bearing 84 via a lubricating oil passage (not shown).

[0051] As shown in FIG. 2 , a flow straightening member 96 is connected to the end surface of the second sub-housing 20 facing the gas turbine engine 200. The flow straightening member 96 has a bottom portion 98, a reduced diameter portion 100, and a top portion 102. The bottom portion 98 facing the second sub-housing 20 is in the shape of a large-diameter, thin-walled cylindrical plate. The top portion 102 facing the gas turbine engine 200 is in the shape of a small-diameter, relatively long cylindrical plate. The reduced diameter portion 100 between the bottom portion 98 and the top portion 102 has a diameter that gradually decreases. Therefore, the flow straightening member 96 has a mountain-like shape or a cup-like shape without a bottom. The outer surface of the reduced diameter portion 100 is smooth and has low surface roughness.

[0052] An inlet 104 is formed in the end surface of the bottom portion 98 facing the second sub-housing 20. The reduced diameter portion 100 is hollow. That is, a relay chamber 106 is formed inside the reduced diameter portion 100. The inlet 104 is an input port for compressed air to enter the relay chamber 106.

[0053] An insertion hole 108 is formed in the top portion 102 along the left-right direction. The diameter (opening diameter) of the insertion hole 108 is larger than the outer diameter of the portion of the second outer stopper 92 that extends along the rotary shaft 40. Therefore, the portion of the second outer stopper 92 that has entered the insertion hole 108 and the outer peripheral wall are spaced apart from the inner wall of the insertion hole 108. In other words, a clearance is formed between the outer peripheral wall of the second outer stopper 92 and the inner wall of the insertion hole 108. This clearance is the second sub-branch passage 942. The width of the relay chamber 106 increases as it approaches the insertion hole 108 and the second sub-branch passage 942.

[0054] Furthermore, the diameter (opening diameter) of the insertion hole 108 is larger than the outer diameter of the left end (small diameter cylindrical portion 242), which has a relatively small diameter, of the compressor wheel 222. Therefore, the small diameter cylindrical portion 242 that has entered the insertion hole 108 also moves away from the inner wall of the insertion hole 108. In other words, a clearance is formed between the outer peripheral wall of the small diameter cylindrical portion 242 and the inner wall of the insertion hole 108. This clearance is the outlet path 943.

[0055] 3, the first insertion hole 78 and the first sub-branched passage 941 communicate with the storage chamber 22. Therefore, the first bearing 74 and the second bearing 84 are exposed to the storage chamber 22.

[0056] The stator 36, together with the rotor 34, constitutes the rotating electric machine 12. The stator 36 has an electromagnetic coil 110 and a plurality of insulating substrates 112. The electromagnetic coils 110 include three types of coils: a U-phase coil, a V-phase coil, and a W-phase coil, which are wound around the insulating substrates 112. When the rotating electric machine 12 is a generator, the rotating electric machine 12 is a so-called three-phase power supply. The plurality of insulating substrates 112 are arranged in an annular shape. This arrangement forms an inner hole in the stator 36.

[0057] The stator 36 is housed in the housing chamber 22. Here, the second sub-housing 20 serves as a stator holder. That is, the second sub-housing 20 has an annular recess 114 formed therein. An insulating base material 112 included in the stator 36 is engaged with the annular recess 114. This engagement positions and fixes the stator 36. Furthermore, the columnar protrusion 76 enters the left opening of the inner hole of the stator 36.

[0058] The inner wall of the storage chamber 22 and the electromagnetic coil 110 are spaced apart from each other by a small distance. This space electrically insulates the main housing 16 and the electromagnetic coil 110.

[0059] A clearance is formed between the outer peripheral wall of the cylindrical protrusion 76 and the insulating substrate 112. A clearance is also formed between the outer wall of the permanent magnet 72 and the inner wall of the electromagnetic coil 110. As will be described later, compressed air, which is a gas, flows through these clearances. In other words, these clearances are part of the compressed air flow path.

[0060] 4, the first sub-housing 18 has an annular protrusion 116 that protrudes in an annular shape. The inside of the annular protrusion 116 forms a hollow recess 118. The protruding tip 46, which is a part of the left end 422 of the inner shaft 42, extends into the hollow recess 118.

[0061] The resolver holder 30 is provided on the annular protrusion 116. The resolver holder 30 has a flange-shaped stopper 120 that protrudes radially outward. The flange-shaped stopper 120 has a diameter larger than the inner diameter of the annular protrusion 116. Therefore, the flange-shaped stopper 120 abuts against the annular protrusion 116. This abutment positions the resolver holder 30. In this state, the resolver holder 30 is connected to the first sub-housing 18 via, for example, a mounting bolt (not shown) or the like.

[0062] In the resolver holder 30, a small cylindrical portion 122 is provided to the left of the flange-shaped stopper 120. In addition, a large cylindrical portion 124 is provided to the right of the flange-shaped stopper 120. The large cylindrical portion 124 has a larger diameter than the small cylindrical portion 122. A retaining hole 126 is formed in the resolver holder 30. Most of the resolver stator 130 is fitted into the retaining hole 126. By this fitting, the resolver stator 130 is held in the resolver holder 30.

[0063] When the large cylindrical portion 124 enters the hollow recess 118 and the flange-shaped stopper 120 abuts against the annular protrusion 116, the resolver rotor 56 is positioned in the inner hole of the resolver stator 130. The resolver stator 130 and the resolver rotor 56 form a resolver 132. The resolver 132 is a rotation parameter detector. In this embodiment, the resolver 132 detects the rotation angle of the inner shaft 42. As described above, the resolver rotor 56 is held by the flange 50 on the left end 422 of the inner shaft 42.

[0064] An engagement hole 134 is formed in the flange-shaped stopper 120. A transmitting connector 136 is engaged with the engagement hole 134. The resolver stator 130 and the transmitting connector 136 are electrically connected via a signal line 138. A receiving connector of a receiver (not shown) is inserted into the transmitting connector 136. The resolver 132 and the receiver are electrically connected via the transmitting connector 136 and the receiving connector. The receiver receives the signal emitted by the resolver 132.

[0065] The small cylindrical portion 122 is provided with a plurality of tab portions 140. One tab portion 140 is shown in FIG. 3. The tab portions 140 are omitted from FIG. 1. Furthermore, a cap cover 32 is placed over the small cylindrical portion 122. The cap cover 32 closes the left opening of the small cylindrical portion 122 and shields the left end portion 422 of the inner shaft 42. The cap cover 32 is connected to the tab portions 140 via a connecting bolt 142.

[0066] As described above, the first casing 26 and the second casing 28 are integrally provided on the side wall near the left end of the main housing 16. The first casing 26 accommodates the U-phase terminal 1441, the V-phase terminal 1442, and the W-phase terminal 1443. The U-phase terminal 1441 is electrically connected to the U-phase coil of the electromagnetic coil 110. The V-phase terminal 1442 is electrically connected to the V-phase coil of the electromagnetic coil 110. The W-phase terminal 1443 is electrically connected to the W-phase coil of the electromagnetic coil 110. The U-phase terminal 1441, the V-phase terminal 1442, and the W-phase terminal 1443 are electrical terminals to which an external device (external load or external power supply) is electrically connected. Electric power generated by the rotating electric machine 12 is supplied to the external device. An example of the external load is a motor (not shown). An example of the external device is a battery 146 shown in FIG. 7.

[0067] The second casing 28 is adjacent to the first casing 26. The second casing 28 houses a thermistor 148, which is a temperature measuring device. Although not shown, the measurement terminal of the thermistor 148 is drawn out from the second casing 28 and then connected to the electromagnetic coil 110. A harness 149 connected to the thermistor 148 is drawn out from the second casing 28 to the outside.

[0068] The internal space of the second casing 28 and the internal space of the first casing 26 are in communication with each other via a communication hole (not shown). The internal space of the first casing 26 is in communication with the storage chamber 22.

[0069] 1 and 2, a current converter 150 is provided on the outer peripheral wall of the main housing 16. As shown in Fig. 7, the current converter 150 has a conversion circuit 152, a capacitor 154, and a control circuit 156. The conversion circuit 152, the capacitor 154, and the control circuit 156 are housed in an equipment case 158. The equipment case 158 is disposed, for example, on the outer peripheral wall of the main housing 16 at a location that does not interfere with the first hollow tube portion 1601, the second hollow tube portion 1602, and the third hollow tube portion 1603 (see Fig. 1).

[0070] The hollow interiors of the first hollow pipe portion 1601, the second hollow pipe portion 1602, and the third hollow pipe portion 1603 are relay communication passages through which compressed air flows. That is, in this embodiment, three relay communication passages are formed in the rotating electrical machine housing 14.

[0071] The conversion circuit 152 includes a power module 161. The conversion circuit 152 converts the AC current generated in the electromagnetic coil 110 into a DC current. At this time, the capacitor 154 temporarily stores the DC current converted by the conversion circuit 152 as an electric charge. The conversion circuit 152 also has the function of converting the DC current sent from the battery 146 into an AC current. In this case, the capacitor 154 temporarily stores the DC current sent from the battery 146 to the electromagnetic coil 110 as an electric charge.

[0072] The control circuit 156 controls the current density of the DC current flowing from the capacitor 154 to the battery 146 or the DC current flowing in the opposite direction. The DC current from the battery 146 is supplied to a motor (neither of which is shown) via an AC-DC converter, for example.

[0073] A compressed air flow path is provided in the rotating electrical machine system 10 configured as above. This compressed air flow path will be described.

[0074] As shown in Fig. 8, the second sub-housing 20 has an annular collecting passage 162 formed as an annular recess on its end surface facing the gas turbine engine 200. As will be described later, part of the compressed air generated by the gas turbine engine 200 flows through the collecting passage 162. Three upstream communication holes 164 are formed in the bottom wall of the collecting passage 162 (annular recess). The upstream communication holes 164 are inlets for compressed air.

[0075] Air relay paths 166 are provided inside the second sub-housing 20. The air relay paths 166 extend radially along the diameter direction of the second sub-housing 20. The air relay paths 166 communicate with the collecting flow path 162 on the outer side in the diameter direction via the upstream communication holes 164. Furthermore, three first downstream communication holes 1681 to 1683 are formed in the end face of the second sub-housing 20 facing the rotating electric machine 12. The first downstream communication holes 1681 to 1683 are first output ports of the air relay path 166. The collecting flow path 162 and the air relay paths 166 form a distribution path.

[0076] Three second downstream communicating holes 1701-1703 are formed in the end face of the second sub-housing 20 facing the gas turbine engine 200. The second downstream communicating holes 1701-1703 are second output ports of the air relay passage 166. The second downstream communicating holes 1701-1703 are located radially inward of the first downstream communicating holes 1681-1683. Therefore, the compressed air that has flowed through the air relay passage 166 is divided into compressed air that enters the first downstream communicating holes 1681-1683 and compressed air that enters the second downstream communicating holes 1701-1703.

[0077] As shown in Fig. 2, a first hollow pipe 1601 to a third hollow pipe 1603 are provided on the outer surface of the side wall of the main housing 16. The first downstream communication holes 1681 to 1683 open individually into the first hollow pipe 1601 to the third hollow pipe 1603, respectively. As can be seen from this, the air relay path 166 communicates between the collecting flow path 162 and the hollow interiors of the first hollow pipe 1601 to the third hollow pipe 1603. As shown in Fig. 3, the first hollow pipe 1601 to the third hollow pipe 1603 are located diametrically outward of the cooling jacket 24 formed inside the side wall of the main housing 16.

[0078] The first to third hollow pipes 1601 to 1603 extend along the axial direction of the main housing 16. The hollow interior of the first hollow pipe 1601 communicates with the internal space of the second casing 28. The hollow interiors of the second hollow pipe 1602 and the third hollow pipe 1603 communicate with the internal space of the first casing 26. As will be described later, the curtain air that has circulated through the hollow interior of the first hollow pipe 1601 flows into the internal space of the second casing 28. The curtain air that has circulated through the hollow interiors of the second hollow pipe 1602 and the third hollow pipe 1603 flows into the internal space of the first casing 26. As can be seen from this, the first casing 26 and the second casing 28 are disposed downstream of the portions of the first to third hollow pipes 1601 to 1603 that are located outside the cooling jacket 24.

[0079] As described above, the internal space of the first casing 26 and the internal space of the second casing 28 are in communication with each other via the interconnecting holes. In addition, the internal space of the first casing 26 is in communication with the storage chamber 22. Therefore, the compressed air that has flowed through the first hollow pipe portion 1601 to the third hollow pipe portion 1603 flows into the storage chamber 22 via the first casing 26.

[0080] In this embodiment, the case where first hollow tube portion 1601 to third hollow tube portion 1603 are provided is illustrated, but the number of hollow tube portions is determined appropriately depending on the flow rate or flow speed required for the curtain air formed from compressed air. That is, the number of hollow tube portions is not limited to three. Similarly, the cross-sectional area of ​​the hollow tube portions is also determined appropriately depending on the flow rate or flow speed required for the curtain air.

[0081] The compressed air that has flowed into the storage chamber 22 is then divided into compressed air flowing toward the first insertion hole 78 and compressed air flowing toward the second insertion hole 86. Specifically, a portion of the compressed air flows through the clearance between the first sub-housing 18 and the rotor 34 and flows toward the first insertion hole 78. In this manner, the clearance between the first sub-housing 18 and the rotor 34 is the first branch path L. On the other hand, the remaining portion of the compressed air flows mainly through the clearance between the outer wall of the permanent magnet 72 and the inner wall of the electromagnetic coil 110 and flows toward the second insertion hole 86. In this manner, the clearance between the outer wall of the permanent magnet 72 and the inner wall of the electromagnetic coil 110 is the second branch path M.

[0082] The compressed air that reaches the first branch path L forms an air curtain that seals in the lubricating oil supplied to the first bearing 74. Furthermore, the compressed air that reaches the second distal end 861 of the second insertion hole 86 from the second branch path M forms an air curtain that seals in the lubricating oil supplied to the second bearing 84. In this way, the compressed air that flows into the storage chamber 22 functions as an air curtain.

[0083] As shown in Fig. 6, three inlets 104 are formed in the bottom portion 98 of the flow straightening member 96. Fig. 6 shows only one of the inlets. One of the inlets 104 communicates with a second downstream communicating hole 1701 (not shown). Another of the inlets 104 communicates with a second downstream communicating hole 1702 (shown). Another of the inlets 104 communicates with a second downstream communicating hole 1703 (not shown). Therefore, compressed air output from the second downstream communicating holes 1701 to 1703 enters the relay chamber 106 of the reduced diameter portion 100 of the flow straightening member 96 via the inlets 104.

[0084] The relay chamber 106 is connected to the insertion hole 108 formed in the top portion 102. The width of the relay chamber 106 increases as it approaches the insertion hole 108 and the second sub-branch path 942. Therefore, as the compressed air flows through the relay chamber 106, the pressure of the curtain air decreases.

[0085] The outlet of the relay chamber 106 faces the small diameter cylindrical portion 242 of the compressor wheel 222. Therefore, the compressed air that enters the relay chamber 106 comes into contact with the small diameter cylindrical portion 242 of the compressor wheel 222. The compressed air is then divided into compressed air that flows toward the second sub-branch path 942 and compressed air that flows toward the outlet path 943. As a result, the pressure of the compressed air that flows along the second sub-branch path 942 toward the second proximal end 862 of the second insertion hole 86 decreases.

[0086] The compressed air that reaches the second proximal end 862 of the second insertion hole 86 from the second sub-branch passage 942 forms an air curtain that seals the lubricating oil supplied to the second bearing 84. In addition, the compressed air that flows into the outlet passage 943 is guided toward the inside of the first end (open end) of the shroud case 220. This compressed air is sucked back into the compressor wheel 222.

[0087] An exhaust path 172 is formed in the main housing 16. The compressed air that has reached the first branch path L and the compressed air that has reached the second branch path M are exhausted to the outside of the main housing 16 via the exhaust path 172.

[0088] Next, the gas turbine engine 200 will be described. As shown in Fig. 9, the gas turbine engine 200 includes an engine housing 202 and an output shaft 204 that rotates within the engine housing 202. The engine housing 202 includes an inner housing 2021 and an outer housing 2022. The inner housing 2021 is connected to the second sub-housing 20 of the rotating electrical machine system 10. The outer housing 2022 is connected to the inner housing 2021. The outer housing 2022 is a housing main body.

[0089] 1 and 8, the inner housing 2021 has a first annular portion 206, a second annular portion 208, and a plurality of leg portions 210. The first annular portion 206 is connected to the second sub-housing 20. The diameter of the second annular portion 208 is larger than the diameter of the first annular portion 206. The leg portions 210 connect the first annular portion 206 and the second annular portion 208. In the illustrated example, the number of legs 210 is six. However, the number of legs 210 is determined depending on the connection strength required between the gas turbine engine 200 and the rotating electrical machine system 10. That is, the number of legs 210 is not limited to six as in the illustrated example.

[0090] A cylindrical cover portion 212 protrudes from a central opening of the second annular portion 208 toward the rotating electrical machine system 10. The right ends of the leg portions 210 are connected to both cylindrical cover portions 212. An intake space 214 is formed between the leg portions 210.

[0091] As shown in Figures 8 and 9, bleed passages 216 are individually formed inside the six leg portions 210. The inlets of the bleed passages 216 are individually formed in the leg portions 210 at the connection points with the cylindrical cover portion 212. The outlets of the bleed passages 216 are individually formed in the end surface of the first annular portion 206 facing the second sub-housing 20. All of the outlets of the bleed passages 216 are located on the circumference of an imaginary circle. Therefore, all of the outlets of the bleed passages 216 overlap with the collecting passage 162, which is formed in an annular shape. In other words, all of the multiple bleed passages 216 are communicated with the collecting passage 162. In this way, compressed air from the multiple bleed passages 216 flows into and collects in the collecting passage 162.

[0092] An air vent hole 217 is formed in the leg portion 210. The air vent hole 217 extends linearly from the inner wall to the outer wall of the cylindrical cover portion 212. The air vent hole 217 can also extend from the inner wall of the cylindrical cover portion 212 to the outer wall of the leg portion 210. There may be one or more air vent holes 217. Furthermore, it is not essential to form the air vent hole 217.

[0093] 9, an annular engaging recess 218 is formed on the right end surface of the second annular portion 208. The engaging recess 218 positions and fixes the shroud case 220 and the diffuser 226 (described later).

[0094] As shown in FIG. 9, the gas turbine engine 200 further includes a shroud case 220 , a compressor wheel 222 , a turbine wheel 224 , a diffuser 226 , a combustor 228 , and a nozzle 230 .

[0095] The shroud case 220 is hollow and larger than the airflow straightening member 96. The small-diameter left end of the shroud case 220 faces the airflow straightening member 96. The large-diameter right end of the shroud case 220 is inserted into the cylindrical cover portion 212 of the inner housing 2021. The diameter of the shroud case 220 gradually decreases from the right end to the left end, but the tip of the left end is curved so as to expand outward in the diameter direction.

[0096] The left end of the shroud case 220 is exposed to the intake space 214. The top portion 102 of the airflow straightening member 96 extends into the interior of the left end of the shroud case 220. An annular closing flange portion 232 is provided on the curved side peripheral wall of the shroud case 220. The outer edge of the closing flange portion 232 abuts against the inner walls of the cylindrical cover portion 212 and the leg portion 210.

[0097] An air bleed port 234 is formed in the side wall of the shroud case 220 between the blocking flange portion 232 and the first engaging protrusion 238. The air bleed port 234 extends from the inner surface to the outer surface of the side wall of the shroud case 220. The air bleed port 234 is an entrance to the chamber 236 through which compressed air enters the chamber 236.

[0098] The chamber 236 is interposed between the bleed port 234 and the bleed passage 216. That is, the chamber 236 connects the bleed port 234 and the bleed passage 216. The chamber 236 is also open to the atmosphere via an air vent hole 217.

[0099] A first engagement protrusion 238 protrudes from the right end of the shroud case 220 toward the second annular portion 208. The first engagement protrusion 238 engages with the engagement recess 218 of the second annular portion 208. This engagement, together with the outer edge of the closing flange portion 232 abutting against the inner walls of the cylindrical cover portion 212 and the leg portion 210, positions and fixes the shroud case 220 to the inner housing 2021. At the same time, a chamber 236 is formed that is surrounded by the leg portion 210, the cylindrical cover portion 212, the second annular portion 208, the closing flange portion 232 of the shroud case 220, the side peripheral wall, and the first engagement protrusion 238. The chamber 236 forms an annular shape surrounding the shroud case 220.

[0100] The compressor wheel 222 and the turbine wheel 224 can rotate integrally with the rotary shaft 40 and the output shaft 204. That is, as shown in detail in FIG. 6 , the compressor wheel 222 has a small-diameter cylindrical portion 242 at its left end. The small-diameter cylindrical portion 242 enters the insertion hole 108 formed in the flow straightening member 96. A first external spline 239 is formed on the inner wall of the small-diameter cylindrical portion 242. The first external spline 239 meshes with the first internal spline 66 formed on the right open end 442 of the outer shaft 44.

[0101] The right open end 442 of the outer shaft 44 is press-fitted into the hollow interior of the small diameter cylindrical portion 242. Therefore, the inner peripheral wall of the left opening of the small diameter cylindrical portion 242 presses the outer peripheral wall of the right open end 442 of the outer shaft 44 radially inward. The compressor wheel 222 is connected to the outer shaft 44 (rotating shaft 40) by the above-mentioned meshing and press-fitting.

[0102] A through hole 240 extending in the left-right direction is formed in the diametric center of the compressor wheel 222. A second external spline 246 is engraved on the inner wall of the left end of this through hole 240. The diameter of the through hole 240 at a portion that communicates with the hollow interior of the small-diameter cylindrical portion 242 is slightly smaller than other portions. For this reason, an inner flange portion 248 is provided in the compressor wheel 222 near the opening of the through hole 240 on the side of the small-diameter cylindrical portion 242. The diameter of the through hole 240 is smallest at the portion where the inner flange portion 248 is provided.

[0103] The output shaft 204 provided on the turbine wheel 224 is inserted into the through hole 240. The left end of the output shaft 204 extends to approximately the same position as the left end of the small diameter cylindrical portion 242 of the compressor wheel 222. As described above, the outer peripheral wall of the right open end 442 of the outer shaft 44 is inserted into the hollow interior of the small diameter cylindrical portion 242. Therefore, the left end of the output shaft 204 protruding from the through hole 240 enters the connecting hole 62 of the rotating shaft 40. A male thread 252 is formed on the left end of the output shaft 204. The male thread 252 is threadedly engaged with a female thread 64 formed on the inner wall of the connecting hole 62. This threaded engagement connects the rotating shaft 40 and the output shaft 204.

[0104] A second internal spline 254 is formed near the left end of the output shaft 204. The second internal spline 254 meshes with a second external spline 246 formed on the inner circumferential wall of the through hole 240. In addition, the left end of the output shaft 204 is press-fitted into the inner flange portion 248.

[0105] 9, a ring member 256 is interposed between the compressor wheel 222 and the turbine wheel 224. The ring member 256 is made of a heat-resistant metal material such as a nickel-based alloy.

[0106] 10 , a fitting hole 258 extending from the compressor wheel 222 to the turbine wheel 224 is formed in the ring member 256. Furthermore, a plurality of (e.g., three) labyrinth-forming protrusions 264 are formed in the outer peripheral wall of the ring member 256. The labyrinth-forming protrusions 264 protrude outward in the diameter direction of the ring member 256 and extend along the circumferential direction of the outer peripheral wall. As will be described later, the labyrinth-forming protrusions 264 prevent the burned fuel (exhaust gas) generated in the combustor 228 from flowing back into the compressor wheel 222.

[0107] An annular protrusion 268 protrudes from the right end surface of the compressor wheel 222 facing the turbine wheel 224. When the left end surface of the ring member 256 seats on the right end surface of the compressor wheel 222, the annular protrusion 268 fits into the fitting hole 258. Meanwhile, the output shaft 204 extends from the left end surface of the turbine wheel 224 facing the compressor wheel 222. A fitting protrusion 270 surrounding the output shaft 204 protrudes from the left end surface. When the right end surface of the ring member 256 seats on the left end surface of the turbine wheel 224, the top surface of the fitting protrusion 270 fits into the fitting hole 258. In this state, a portion of each of the compressor wheel 222 and the turbine wheel 224 is fitted into the fitting hole 258. In this state, the ring member 256 is sandwiched between the compressor wheel 222 and the turbine wheel 224.

[0108] The labyrinth-forming protrusion 264 is surrounded by an intermediate plate 266 within the hollow interior of the outer housing 2022 (see FIG. 9 ). The labyrinth-forming protrusion 264 is inserted into a hole 272 formed in the intermediate plate 266. A labyrinth flow path is formed by the inner wall of the hole 272 and the labyrinth-forming protrusion 264 abutting against this inner wall. Compressed air generated by the compressor wheel 222 reaches the labyrinth-forming protrusion 264 via the back surface of the compressor wheel 222. Meanwhile, combustion gas from the turbine wheel 224 reaches the labyrinth-forming protrusion 264. Because the pressure of the compressed air is higher than the pressure of the combustion gas, the combustion gas can be prevented from passing through the labyrinth-forming protrusion 264 and flowing into the space surrounding the compressor wheel 222.

[0109] 9 , within the hollow interior of the outer housing 2022, portions of the shroud case 220 and the compressor wheel 222, and the intermediate plate 266 are surrounded by the diffuser 226. A second engagement protrusion 273 is formed on the left end of the diffuser 226. The second engagement protrusion 273, together with the first engagement protrusion 238 of the shroud case 220, is engaged with the engagement recess 218. Due to this engagement, the diffuser 226 is positioned and fixed to the inner housing 2021.

[0110] Within the hollow interior of the outer housing 2022, the turbine wheel 224 is surrounded by a nozzle 230, which is in turn surrounded by a combustor 228. An annular combustion air passage 274 is formed between the combustor 228 and the outer housing 2022. The combustion air passage 274 is a passage through which combustion air flows. A fuel supply nozzle 275 is positioned and fixed to the right end face of the outer housing 2022. The fuel supply nozzle 275 supplies fuel to the combustor 228.

[0111] The combustor 228 is formed with relay holes 276 that connect the combustion air flow passage 274 with the interior of the combustor 228. As will be described later, combustion air compressed by the compressor wheel 222 passes through the diffuser 226, the combustion air flow passage 274, and the relay holes 276 and reaches the interior of the combustor 228. The combustor 228 is also formed with fine holes (not shown). The air discharged from the fine holes forms an air curtain that cools the interior of the combustor 228.

[0112] The nozzle 230 has a portion surrounding the largest diameter portion of the turbine wheel 224. This portion is formed with a delivery hole (not shown) for supplying combusted fuel together with combustion air to the turbine wheel 224. Note that, hereinafter, combusted fuel will also be referred to as "burned fuel." "Burned fuel" is synonymous with "combustion gas" or "exhaust gas after combustion."

[0113] An exhaust port 280 opens at the right ends of the outer housing 2022 and the nozzle 230. The burned fuel passes through the delivery holes and enters the nozzle 230, and is then blown out of the outer housing 2022 through the exhaust port 280 by the rotating turbine wheel 224. Although not specifically shown, the exhaust port 280 is provided with a discharge pipe for discharging the burned fuel.

[0114] The rotating electrical machine system 10 and the combined power system 400 according to this embodiment are basically configured as described above. Next, the effects of the rotating electrical machine system 10 and the combined power system 400 will be described.

[0115] To start the operation of the combined power system 400, first, a known starter (not shown) rotates the rotating shaft 40. Alternatively, the rotating shaft 40 may be rotated by supplying power from the battery 146.

[0116] The latter case will be described. In this case, a direct current is supplied from the battery 146. The conversion circuit 152 of the current converter 150 shown in FIGS. 2 and 7 converts this direct current into an alternating current. The alternating current is supplied to the electromagnetic coils 110 (the U-phase coil, the V-phase coil, and the W-phase coil) via the U-phase terminal 1441, the V-phase terminal 1442, and the W-phase terminal 1443. When the alternating current flows through the electromagnetic coils 110, an alternating magnetic field is generated in the stator 36. Therefore, an attractive force and a repulsive force act alternately between the electromagnetic coil 110 and the permanent magnet 72 of the rotor 34. As a result, the rotating shaft 40 starts to rotate.

[0117] As shown in FIG. 6 , a first internal spline 66 is formed on the outer peripheral wall of the right open end 442 of the outer shaft 44, and a first external spline 239 is formed on the inner wall of the small-diameter cylindrical portion 242 of the compressor wheel 222. The first internal spline 66 and the first external spline 239 mesh with each other. Furthermore, a second internal spline 254 is formed on the output shaft 204, and a second external spline 246 is formed on the inner wall of the through hole 240 of the compressor wheel 222. The second internal spline 254 and the second external spline 246 mesh with each other. Therefore, the rotational torque of the rotating shaft 40 is quickly transmitted to the output shaft 204 via the compressor wheel 222.

[0118] That is, when the rotating shaft 40 starts to rotate, the output shaft 204 also starts to rotate integrally with the rotating shaft 40. Accordingly, the compressor wheel 222 and the turbine wheel 224 supported on the output shaft 204 rotate integrally with the output shaft 204. As described above, by meshing the first internal spline 66 with the first external spline 239 and meshing the second internal spline 254 with the second external spline 246, the rotational torque of the rotating shaft 40 can be sufficiently transmitted to the output shaft 204.

[0119] Moreover, the right end of the rotating shaft 40 is press-fitted into the hollow interior of the small-diameter cylindrical portion 242 of the compressor wheel 222. In addition, the left end of the output shaft 204 is press-fitted into the inner flange portion 248 of the compressor wheel 222. Therefore, the axis of the rotating shaft 40 and the axis of the output shaft 204 are precisely aligned. This sufficiently prevents the output shaft 204 from rotating eccentrically or vibrating.

[0120] In addition, as shown in Figure 10, a ring member 256 is interposed between the compressor wheel 222 and the turbine wheel 224. An annular protrusion 268 on the right end surface of the compressor wheel 222 and a mating protrusion 270 on the left end surface of the turbine wheel 224 are fitted into a fitting hole 258 of the ring member 256. This fitting also contributes to suppressing eccentric rotation (vibration) of the output shaft 204. Therefore, there is no particular need to provide a mechanism for suppressing vibration. There is also no particular need to increase the diameter of the output shaft 204. This allows the combined power system 400 to be made more compact.

[0121] Furthermore, a frictional force is generated between the right end surface of the compressor wheel 222 and the left end surface of the ring member 256. A frictional force is also generated between the right end surface of the ring member 256 and the left end surface of the turbine wheel 224. This frictional force causes the compressor wheel 222, the ring member 256, and the turbine wheel 224 to adhere to one another. Therefore, rotational misalignment between the two wheels 222, 224 is prevented.

[0122] Furthermore, when assembling the compound power system 400, the above-described fitting allows the compressor wheel 222 and the turbine wheel 224 to be aligned (centered) with respect to the output shaft 204. In this manner, it is preferable to provide a ring member 256 between the two wheels 222, 224, and to individually fit portions of the two wheels 222, 224 into fitting holes 258 of the ring member 256. This makes it easy to center the compressor wheel 222 and the turbine wheel 224 with respect to the output shaft 204.

[0123] As a result of the rotation, as shown in FIG. 9 , air is drawn into the shroud case 220 through the air intake space 214 between the legs 210 of the inner housing 2021. Here, the airflow rectifying member 96 is located at the diametric center of the inner housing 2021. As described above, the airflow rectifying member 96 has a mountain-like shape that narrows in diameter toward the shroud case 220. Furthermore, the surface of the narrowing diameter portion 100 is smooth. Therefore, the drawn air is rectified by the airflow rectifying member 96 so as to be directed toward the shroud case 220. Because the right end of the airflow rectifying member 96 enters the left end opening of the shroud case 220, the air is efficiently guided into the shroud case 220. In this way, by giving the airflow rectifying member 96 the shape described above and having the top portion 102 enter the shroud case 220, the air can be efficiently collected by the shroud case 220.

[0124] The air drawn into the shroud case 220 flows between the compressor wheel 222 and the shroud case 220. Because the space between the compressor wheel 222 and the shroud case 220 is sufficiently narrow compared to the left opening of the shroud case 220, the air is compressed as it flows through the shroud case 220. In other words, compressed air is generated.

[0125] Shroud case 220 is formed with an air bleed port 234. Therefore, part of the compressed air is diverted from air bleed port 234 as curtain air and flows into chamber 236. Chamber 236 is annular, and has a volume larger than the volume of air bleed port 234. Therefore, the curtain air that flows into chamber 236 is temporarily stored in chamber 236.

[0126] Since a plurality of bleed passages 216 are formed, compressed air is distributed from the chamber 236 to each bleed passage 216. In this case, the pressure of the distributed curtain air may differ. However, in this embodiment, the compressed air (curtain air) that has passed through the bleed port 234 flows into the single annular chamber 236. This makes the pressure of the curtain air in the chamber 236 uniform. In other words, the pressure of the curtain air is made uniform. In this way, the chamber 236 is a pressure adjustment chamber that adjusts the pressure of the curtain air to a substantially constant value.

[0127] As described above, the curtain air flowing in from the bleed port 234 is part of the compressed air and is under high pressure. Here, since the volume of the chamber 236 is larger than the volume of the bleed port 234, the curtain air diffuses as it flows into the chamber 236. This reduces the pressure of the curtain air. As can be seen from this, the chamber 236 also serves as a buffer chamber that reduces the pressure of the compressed air.

[0128] In addition to the bleed passage 216, the inner housing 2021 is also formed with an air vent hole 217. Excess compressed air is released to the outside of the gas turbine engine 200 (to the atmosphere) through the air vent hole 217. This prevents the pressure of the curtain air in the chamber 236 from increasing excessively. In other words, the air vent hole 217 makes it possible to easily adjust the pressure in the chamber 236.

[0129] The inlets of the bleed passages 216 formed individually in each of the six legs 210 open within the chamber 236. Therefore, the curtain air within the chamber 236 then flows individually through the six bleed passages 216, and thereby travels toward the second sub-housing 20. As described above, the pressure of the curtain air is approximately constant at this point.

[0130] 8, the outlets of the six bleed passages 216 all overlap with the collecting passage 162. Therefore, the curtain air that has flowed through the six bleed passages 216 flows into the collecting passage 162 and collects there, and then diffuses in an annular shape along the collecting passage 162. In this process, the pressure of the curtain air is further uniformed.

[0131] The curtain air further flows from the collecting flow path 162 into the three upstream communication holes 164 individually, and circulates along the three air relay paths 166 individually. Then, a portion of the curtain air is discharged from the first downstream communication holes 1681-1683. The remainder of the curtain air is discharged from the second downstream communication holes 1701-1703. Hereinafter, the curtain air discharged from the first downstream communication holes 1681-1683 will be referred to as "first diverted air." The curtain air discharged from the second downstream communication holes 1701-1703 will be referred to as "second diverted air."

[0132] The path of the first diverted air will be described. The first downstream communicating hole 1681 is connected to the hollow interior of the first hollow pipe portion 1601. The first downstream communicating hole 1682 is connected to the hollow interior of the second hollow pipe portion 1602. The first downstream communicating hole 1683 is connected to the hollow interior of the third hollow pipe portion 1603. Therefore, the first diverted air flows through the hollow interiors of the first hollow pipe portion 1601 to the third hollow pipe portion 1603 shown in FIG. 1 etc., and flows from the second end to the first end of the rotating electric machine housing 14.

[0133] The first hollow pipe portion 1601 to the third hollow pipe portion 1603 are located on the outer periphery of the cooling jacket 24. A cooling medium is already circulated through the cooling jacket 24. Therefore, as the first diverted air flows along the first hollow pipe portion 1601 to the third hollow pipe portion 1603, heat of the first diverted air is sufficiently conducted to the cooling medium. This reduces the temperature of the first diverted air to a relatively low temperature. That is, in this embodiment, the cooling jacket 24, which cools the rotating electric machine 12, the current converter 150, and the like, can lower the temperature of the first diverted air. Therefore, there is no need to provide separate cooling equipment for cooling the curtain air in the gas turbine engine 200 or the rotating electric machine system 10. This eliminates the need to provide separate cooling equipment for cooling the curtain air in the gas turbine engine 200 or the rotating electric machine system 10. This allows the combined power system 400 to be made more compact.

[0134] The first diverted air that has flowed through the first hollow pipe portion 1601 flows into the internal space of the second casing 28, as shown in FIG. 2. This forms an air curtain inside the second casing 28. The excess first diverted air flows into the hollow interior (internal space) of the first casing 26 through the interconnecting holes. On the other hand, the first diverted air that has flowed through each of the second hollow pipe portion 1602 and the third hollow pipe portion 1603 flows into the internal space of the first casing 26. Therefore, inside the first casing 26, an air curtain is formed by the first diverted air that has flowed through the second hollow pipe portion 1602 and the third hollow pipe portion 1603.

[0135] As shown in Fig. 3, the excess first diverted air in the first casing 26 flows into the storage chamber 22 formed in the main housing 16. As can be understood from this, the internal spaces of the first casing 26 and the second casing 28 are upstream in the flow path of the first diverted air. The storage chamber 22 of the main housing 16 is downstream in the flow path of the first diverted air.

[0136] The first casing 26 and the second casing 28 are disposed at the first end (left end) of the main housing 16. Therefore, the first diverted air flows in from the left end of the storage chamber 22. The first diverted air then enters the clearance between the outer peripheral wall of the cylindrical protrusion 76 and the insulating base material 112. This clearance is the inner hole of the stator 36.

[0137] A portion of the first diverted air then flows toward the first insertion hole 78 via the first branch path L. The remainder of the first diverted air flows toward the second insertion hole 86 via the second branch path M, along the clearance between the outer wall of the permanent magnet 72 and the inner wall of the electromagnetic coil 110. In this way, the first diverted air branches into compressed air flowing toward the first insertion hole 78 at the left end (first end) and compressed air flowing toward the second insertion hole 86 at the right end (second end).

[0138] A portion of the first diverted air flowing toward the first insertion hole 78 reaches the first proximal end 782 of the first insertion hole 78. At this first proximal end 782, this portion of the first diverted air becomes an air curtain for the first bearing 74. Meanwhile, the remainder of the first diverted air flowing toward the second insertion hole 86 passes through the first sub-branch path 941 and reaches the second distal end 861 of the second insertion hole 86. At this second distal end 861, this portion of the first diverted air becomes an air curtain for the second bearing 84.

[0139] The path of the second diverted air will now be described. The second downstream communication holes 1701-1703 overlap with three inlets 104 formed in the bottom portion 98 of the rectifying member 96. Therefore, the second diverted air flows into the relay chamber 106 (the hollow interior of the rectifying member 96) through the inlets 104.

[0140] As described above, the outlet of the relay chamber 106 opens at a position facing the small diameter cylindrical portion 242 of the compressor wheel 222. Therefore, the second diverted air that flows into the relay chamber 106 comes into contact with the small diameter cylindrical portion 242. A portion of the second diverted air then flows toward the second sub-branch path 942. The remainder of the second diverted air flows toward the outlet path 943.

[0141] A portion of the second diverted air reaches the second proximal end 862 of the second insertion hole 86 via the second sub-branch passage 942. At the second proximal end 862, the portion of the second diverted air becomes an air curtain for the second bearing 84. In this manner, the second bearing 84 is sandwiched between the remainder of the second diverted air that has reached the second proximal end 862 and the portion of the first diverted air that has reached the second distal end 861.

[0142] The remainder of the second diverted air is discharged through the outlet passage 943 to the inside of the left end of the shroud case 220. As described above, air is being drawn into the opening at the left end of the shroud case 220. Therefore, the remainder of the second diverted air is compressed by the compressor wheel 222 together with the drawn-in atmospheric air.

[0143] As described above, air curtains are formed in the second branched path M, the first sub-branched path 941, and the second sub-branched path 942. These air curtains prevent the lubricating oil from entering the internal spaces of the first casing 26 and the second casing 28. That is, the curtain air (first diverted air and second diverted air) prevents the lubricating oil from scattering from the first bearing 74 and the second bearing 84. This prevents the lubricating oil from adhering to the U-phase terminal 1441, the V-phase terminal 1442, the W-phase terminal 1443, the thermistor 148, and the like. In other words, it is possible to prevent the electrical terminals, the measuring device (thermistor 148), and the like from being soiled with the lubricating oil.

[0144] The excess first diverted air passes through the storage chamber 22 and reaches the exhaust path 172. The excess second diverted air flows from the second end to the first end of the main housing 16, for example, via a clearance between the inner wall of the storage chamber 22 and the electromagnetic coil 110. Thereafter, the excess second diverted air reaches the exhaust path 172. The first diverted air and second diverted air that have reached the exhaust path 172 are collected by a collection device (not shown).

[0145] As described above, the pressure of the curtain air is made uniform by the chamber 236 provided between the inner housing 2021 and the shroud case 220. Therefore, the occurrence of pressure distribution in the curtain air is avoided. Furthermore, the occurrence of surging in the curtain air is also avoided. Therefore, it is possible to supply the curtain air to the periphery of the first bearing 74 and the second bearing 84 while maintaining the pressure of the curtain air substantially constant.

[0146] As described above, the width of the relay chamber 106 increases as it approaches the second sub-branch path 942. Moreover, the second diverted air flowing out of the relay chamber 106 is divided into a portion that flows toward the second sub-branch path 942 and a remainder that flows toward the outlet path 943. Therefore, the pressure of the second diverted air that has reached the second proximal end 862 is lower than the pressure of the second diverted air before it flows into the relay chamber 106. As a result, the pressure of the first diverted air that has reached the second distal end 861 and the pressure of the second diverted air that has reached the second proximal end 862 are balanced.

[0147] Compressed air that passes between the shroud case 220 and the compressor wheel 222 without entering the bleed port 234 becomes combustion air. As shown in Fig. 9, the combustion air flows into the diffuser 226. The combustion air flows from an outlet hole formed in the wall of the diffuser 226 into a combustion air flow passage 274 between the combustor 228 and the outer housing 2022. The combustion air further flows into the combustion chamber (the hollow interior of the combustor 228) through a relay hole 276 formed in the combustor 228, the fine holes, the clearance between the combustor 228 and the fuel supply nozzle 275, and the like.

[0148] The combustor 228 is preheated. Therefore, the combustion chamber is also at a high temperature. Fuel is supplied to the high-temperature combustion chamber from the fuel supply nozzle 275. The fuel burns together with the combustion air, producing high-temperature burned fuel. When this burned fuel is supplied into the nozzle 230 from the delivery holes, it expands within the nozzle 230. This causes the turbine wheel 224 to begin rotating at a high speed.

[0149] The output shaft 204 holds a turbine wheel 224. A compressor wheel 222 is also provided on the output shaft 204. Therefore, as the turbine wheel 224 rotates at high speed, the output shaft 204 and the compressor wheel 222 rotate integrally at high speed. At the same time, the rotating shaft 40 also rotates at high speed. The burned fuel is discharged to the outside of the outer housing 2022 through a discharge pipe (not shown) provided at the discharge port 280.

[0150] The ring member 256 interposed between the compressor wheel 222 and the turbine wheel 224 also serves as a sealing member that seals the gap between the two wheels 222, 224. Furthermore, as shown in FIG. 10 , a plurality of labyrinth-forming protrusions 264 are formed on the outer peripheral wall of the ring member 256. The labyrinth-forming protrusions 264 abut against the inner walls of holes 272 formed in the intermediate plate 266. Compressed air generated by the compressor wheel 222 reaches the labyrinth-forming protrusions 264 via the back surface of the compressor wheel 222. Furthermore, combustion gas from the turbine wheel 224 reaches the labyrinth-forming protrusions 264. As described above, the pressure of the compressed air is higher than the pressure of the combustion gas. This prevents the combustion gas from passing through the labyrinth-forming protrusions 264 and flowing into the compressor wheel 222. For the reasons described above, the burnt fuel is prevented from entering the through-hole 240 from between the wheels 222, 224, for example.

[0151] 9, when output shaft 204 starts to rotate at high speed, the supply of current from battery 146 (see FIG. 7) to electromagnetic coil 110 is stopped. However, because turbine wheel 224 is already rotating at high speed as described above, rotating shaft 40 rotates at high speed integrally with turbine wheel 224 and output shaft 204. Even at this time, for the same reason as described above, sufficient rotational torque is transmitted from output shaft 204 to rotating shaft 40.

[0152] 3, the rotation direction of the output shaft 204 and the rotating shaft 40 is preferably opposite to the rotation direction when the small cap nut 58, the large cap nut 60, and the male thread 252 are screwed together. In this case, the small cap nut 58, the large cap nut 60, and the male thread 252 are prevented from loosening during rotation of the rotating shaft 40. Note that the small cap nut 58, the large cap nut 60, or the male thread 252 may be provided with a mechanism to prevent loosening.

[0153] Because the rotating shaft 40 holds the permanent magnet 72, an AC current is generated in the electromagnetic coil 110 surrounding the permanent magnet 72. The AC current is sent to the current converter 150 shown in FIGS. 2 and 7 via a U-phase terminal 1441, a V-phase terminal 1442, and a W-phase terminal 1443. A conversion circuit 152 of the current converter 150 converts this AC current into a DC current. When a control circuit 156 of the current converter 150 determines that the output of an external load (e.g., a motor) electrically connected to the battery 146 has decreased, the control circuit 156 supplies a DC current to the battery 146 (see FIG. 7) via a capacitor 154. This charges the battery 146.

[0154] The electromagnetic coil 110 generates heat as current flows through it. Here, a portion of the first diverted air comes into contact with the left end of the stator 36. Furthermore, the remaining portion of the first diverted air, which passes through the storage chamber 22 and heads toward the second insertion hole 86, comes into contact with the outer and inner walls of the stator 36. Therefore, the stator 36 is cooled by the first diverted air. Furthermore, a cooling medium flows through the cooling jacket 24 provided on the main housing 16. The rotating electric machine 12 is quickly cooled by this cooling medium.

[0155] In this embodiment, the rotating electric machine housing 14 (main housing 16) that houses the rotating electric machine 12 and the first casing 26 that houses the U-phase terminal 1441, the V-phase terminal 1442, and the W-phase terminal 1443 are provided separately. Therefore, the heat generated in the stator 36 in the main housing 16 is unlikely to affect the U-phase terminal 1441, the V-phase terminal 1442, and the W-phase terminal 1443 in the first casing 26. Note that the U-phase terminal 1441, the V-phase terminal 1442, and the W-phase terminal 1443 also generate heat when current is applied. However, the U-phase terminal 1441, the V-phase terminal 1442, and the W-phase terminal 1443 are quickly cooled by the first diverted air flow supplied to the first casing 26.

[0156] In this way, the first diverted air also serves to cool heat-generating locations in the rotating electric machine system 10. Because the electrical terminals (U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443), the electromagnetic coil 110, the permanent magnet 72, etc. are cooled, the influence of heat on the output control of the rotating electric machine system 10, etc. is avoided. In addition, a decrease in the excitation of the electromagnetic coil 110, the permanent magnet 72, etc. due to heat is also avoided. As a result, the reliability of the rotating electric machine system 10 is improved.

[0157] Furthermore, because the main housing 16 that houses the rotating electric machine 12 and the first casing 26 that houses the U-phase terminal 1441, the V-phase terminal 1442, and the W-phase terminal 1443 are provided separately, the rotating electric machine 12 and the electrical terminals are spaced apart from each other. Therefore, the U-phase terminal 1441, the V-phase terminal 1442, and the W-phase terminal 1443 are less susceptible to the effects of vibrations that occur as the rotor 34 rotates. In other words, the U-phase terminal 1441, the V-phase terminal 1442, and the W-phase terminal 1443 are protected from vibrations. Furthermore, as described above, the lubricating oil in the first bearing 74 and the second bearing 84 prevents seizure. Therefore, the rotating electric machine system 10 has excellent durability.

[0158] While the rotating shaft 40 is rotating, the rotation angle (rotation parameter) of the rotating shaft 40 is detected by the resolver 132. Specifically, the resolver rotor 56 attached to the left end 422 of the inner shaft 42 rotates integrally with the rotating shaft 40. As a result, an electrical signal generated in the resolver stator 130 is transmitted to the receiver via the transmitting connector 136. The receiver reads the electrical signal and calculates the rotation angle of the rotating shaft 40 based on the electrical signal. The receiver sends the calculation result to a control device or the like (not shown). The control device or the like calculates the rotation speed based on this rotation angle.

[0159] In the rotating electrical machine system 10, a first spigot fitting portion 571 is formed between the inner shaft 42 and the outer shaft 44. In addition, in the rotating electrical machine system 10, a second spigot fitting portion 572 is formed between the large cap nut 60 (restraint member) and the outer shaft 44. Therefore, the inner shaft 42 is restrained by the outer shaft 44. For this reason, the inner shaft 42 is unlikely to become eccentric with respect to the outer shaft 44. As a result, when the rotor 34 rotates, vibration of the inner shaft 42 with respect to the outer shaft 44 is suppressed.

[0160] This suppresses the resolver rotor 56 from rotating eccentrically relative to the resolver stator 130. Also, vibration of the resolver rotor 56 due to vibration of the inner shaft 42 is suppressed. Furthermore, the first bearing 74 and the second bearing 84 that support the rotating shaft 40 are provided inside the rotating electric machine housing 14. Therefore, the rotating electric machine housing 14 suppresses vibration of the first bearing 74 and the second bearing 84. This further suppresses vibration of the resolver 132.

[0161] Furthermore, the resolver 132 is disposed at the protruding tip 46 exposed from the rotary electric machine housing 14. Therefore, the resolver 132 is less susceptible to the effects of heat generated in the electromagnetic coil 110 of the stator 36 inside the rotary electric machine housing 14.

[0162] As described above, in this embodiment, the transfer of heat, vibrations, and the like to the resolver 132 is suppressed. This enables the resolver 132 to accurately calculate the rotation angle of the rotating shaft 40. In other words, the detection result of the rotation angle by the resolver 132 becomes accurate. In addition, the life of the resolver 132 is also extended.

[0163] For the reasons described above, even if the diameter of the rotating shaft 40 is small, the rotation parameters of the rotating shaft 40 can be accurately calculated. Therefore, the rotating electric machine system 10 and the combined power system 400 can be made smaller.

[0164] There may be cases where the resolver 132 is replaced with another resolver having a larger inner diameter and outer diameter. If a single solid rotating shaft is used as the rotating shaft, replacing it with a resolver having a larger inner diameter and outer diameter requires replacing it with a larger-diameter solid rotating shaft. In this case, it is not easy to pass the large-diameter solid rotating shaft through the first bearing 74 and the second bearing 84.

[0165] In this embodiment, the rotating shaft 40 is made up of the outer shaft 44 and the inner shaft 42. The outer shaft 44 is passed through the first bearing 74 and the second bearing 84, and the resolver rotor 56 is provided on the portion of the inner shaft 42 that is exposed from the outer shaft 44. Therefore, when replacing the resolver 132 with another resolver having larger inner and outer diameters, this can be achieved by simply replacing the inner shaft 42 with an inner shaft having a larger diameter at the left end 422. As can be seen from this, according to this embodiment, by replacing the inner shaft 42, it is possible to accommodate resolvers with various inner and outer diameters.

[0166] As described above, the present embodiment is a rotating electric machine system (10) including a rotating electric machine (12) and a rotating electric machine housing (14) that rotatably supports a rotating shaft (40) of the rotating electric machine, The rotating shaft has a hollow cylindrical outer shaft (44) and an inner shaft (42) removably inserted into the hollow interior of the outer shaft, The outer shaft has a first outer shaft end portion (441) and a second outer shaft end portion (442) positioned opposite to each other in the axial direction of the rotating shaft, The inner shaft has a first inner shaft end portion (421) and a second inner shaft end portion (422) positioned opposite to each other in the axial direction, the first inner shaft end of the inner shaft has a protruding tip (46) exposed from the first outer shaft end of the outer shaft; a rotation parameter detector (132) provided at the protruding tip to detect a rotation parameter of the rotating shaft; a holding member (30) provided at the protruding tip and supporting the rotation parameter detector at the protruding tip; a restraining member (60) provided at the protruding tip and restraining the inner shaft to the outer shaft; A rotating electrical machine system comprising:

[0167] In this embodiment, the inner shaft is restrained to the outer shaft by the restraining member, which makes it difficult for the inner shaft to become eccentric with respect to the outer shaft, thereby suppressing vibration of the rotating shaft even when the rotating shaft is rotated at high speed.

[0168] This allows the rotating shaft to rotate at high speed when the rotating electrical machine system is miniaturized, thereby increasing the amount of power generation. Also, the life of the rotation parameter detector can be extended.

[0169] In this embodiment, a first thread (552) is formed on the outer surface of the inner shaft, The restraining member has a second screw (611) that screws into the first screw and an accommodating hole (612) in which the first outer shaft end is accommodated, and the rotating electric system is disclosed in which the restraining member and the first outer shaft end are spigot-fitted together by accommodating the first outer shaft end in the accommodating hole.

[0170] In this case, a spigot-fit portion is formed between the restraining member and the end of the first outer shaft, which makes it even more difficult for the inner shaft to become eccentric relative to the outer shaft.

[0171] This embodiment discloses a rotary electric machine system in which the first inner shaft end portion and the first outer shaft end portion are spigot-fitted together.

[0172] In this case, a spigot-fit portion is formed between the first inner shaft end portion and the first outer shaft end portion, making it even more difficult for the inner shaft to become eccentric with respect to the outer shaft.

[0173] In this embodiment, a first thread is formed on the outer surface of the inner shaft, the restraining member has a second screw that is screwed onto the first screw and an accommodating hole that accommodates the first outer shaft end, and the restraining member and the first outer shaft end are spigot-fitted together by accommodating the first outer shaft end in the accommodating hole, A rotating electrical machine system is disclosed in which the first inner shaft end and the first outer shaft end are spigot-fitted together.

[0174] In this case, a spigot fitting portion is formed between the restraining member and the first outer shaft end, and a spigot fitting portion is formed between the first inner shaft end and the first outer shaft end. By forming two spigot fitting portions in this way, it is possible to prevent the inner shaft from becoming eccentric with respect to the outer shaft.

[0175] A suitable example of the rotation parameter detector is a resolver. That is, this embodiment discloses a rotating electrical machine system in which the rotation parameter detector is a resolver (132) including a resolver rotor (56) and a resolver stator (130), and the resolver rotor is attached to the protruding tip.

[0176] This embodiment discloses a rotating electric machine system in which the holding member is provided with a transmitting connector (136), and the transmitting connector electrically connects the rotation parameter detector to a receiver that receives a signal emitted by the rotation parameter detector.

[0177] In this case, the transmitting connector can be positioned and fixed to the holding member.

[0178] This embodiment discloses a hybrid power system (400) including the rotating electric machine system (10) configured as described above and an internal combustion engine (200). Here, the internal combustion engine has an output shaft (204) that rotates integrally with the rotating shaft of the rotating electric machine system. The output shaft is connected to at least one of the second outer shaft end and the second inner shaft end.

[0179] As the rotating electrical machine system becomes smaller, the combined power system also becomes smaller, and the smaller combined power system becomes lighter.

[0180] The present invention is not limited to the above-described embodiment, and various configurations can be adopted without departing from the gist of the present invention.

[0181] For example, in this embodiment, the resolver 132 is used as the rotation parameter detector, but it is also possible to use a detector including a Hall element.

[0182] In the gas turbine engine 200, the compressor wheel 222 and the turbine wheel 224 may be arranged in the opposite direction to that shown in Figure 9. In this case, a through hole 240 may be formed in the turbine wheel 224, and the compressor wheel 222 may be provided with the output shaft 204. Alternatively, the compressor wheel 222 and the turbine wheel 224 may be of a centrifugal type or an axial flow type. As long as the compressor wheel 222 and the turbine wheel 224 are arranged on the same axis, a combination of a centrifugal type and an axial type multi-stage compressor wheel and a multi-stage turbine wheel may be used.

[0183] 3, the rotating electric machine 12 constituting the rotating electric machine system 10 may be a motor in which the rotating shaft 40 rotates when current is applied to the electromagnetic coil 110. In this case, the U-phase terminal 1441, the V-phase terminal 1442, and the W-phase terminal 1443 are electrical terminal portions that receive power from the battery 146.

[0184] The rotating electrical machine system 10 can also be used independently, separated from the gas turbine engine 200. If it is necessary to supply compressed air to the rotating electrical machine system 10, a compression pump can be provided outside the rotating electrical machine housing 14 and used as the gas supply source. [Explanation of symbols]

[0185] 10... Rotating electric machine system 12... Rotating electric machine 14... Rotating electric machine housing 16... Main housing 18...First sub-housing 20...Second sub-housing 22...Storage room 24...Cooling jacket 26...First casing 28...Second casing 30...Resolver holder 34...Rotor 36... Stator 40... Rotating shaft 42...Inner shaft 44...Outer shaft 46...Protruding tip 56...Resolver rotor 60...Large cap nut 62...Connecting hole 72...Permanent magnet 74...First bearing 84... Second bearing 96... Flow straightening member 110... electromagnetic coil 130... resolver stator 132...Resolver 134...Engagement hole 136...Transmitting connector 138...Signal line 146...Battery 148...Thermistor 149...Harness 162...Collecting flow path 164...Upstream communication hole 166...Air relay path 172...Exhaust passage 200...Gas turbine engine 202...engine housing 204...output shaft 210: Leg portion; 212: Cylindrical cover portion 214...intake space 216...bleed passage 217...Air vent hole 220...Shroud case 222...Compressor wheel 224...Turbine wheel 226... Diffuser 228... Combustor 230...Nozzle 234...Bleed port 256...Ring member 400...Composite power system 422...First end of inner shaft 423...Second end of inner shaft 441...First open end of outer shaft 442...Second open end of outer shaft 471... Equal diameter section 552... Second external thread 571...First spigot fitting portion 572...Second spigot fitting portion 611...Internal thread 612...Accommodating hole 781...Distal end of first insertion hole 782...Proximal end of first insertion hole 861...Distal end of second insertion hole 862...Proximal end of second insertion hole 943...Exit path 1441...U phase terminal 1442...V phase terminal 1443...W phase terminal 1601~1603...1st~3rd hollow tube section 1681~1683...First downstream communication hole 1701~1703...Second downstream communication hole 2021...Inner housing 2022...Outer housing

Claims

1. A rotating electric machine system including a rotating electric machine and a rotating electric machine housing that rotatably supports a rotating shaft of the rotating electric machine, The rotating shaft has a hollow cylindrical outer shaft and an inner shaft that is removably inserted into the hollow interior of the outer shaft, the outer shaft has a first outer shaft end portion and a second outer shaft end portion located opposite to each other in the axial direction of the rotating shaft, the inner shaft has a first inner shaft end portion and a second inner shaft end portion positioned opposite to each other in the axial direction, the first inner shaft end of the inner shaft has a protruding tip exposed from the first outer shaft end of the outer shaft, a rotation parameter detector provided at the protruding tip to detect a rotation parameter of the rotating shaft; a holding member provided at the protruding tip to support the rotation parameter detector at the protruding tip; a restraining member provided at the protruding tip end and configured to restrain the inner shaft to the outer shaft; A rotating electric machine system comprising:

2. 2. The rotating electrical machine system according to claim 1, wherein a first thread is formed on an outer surface of the inner shaft, The restraining member has a second screw that threads onto the first screw and an accommodating hole in which the first outer shaft end is accommodated, and the first outer shaft end is accommodated in the accommodating hole, thereby forming a spigot-fit between the restraining member and the first outer shaft end.

3. 3. The rotating electrical machine system according to claim 1, wherein the first inner shaft end portion and the first outer shaft end portion are spigot-fitted together.

4. 2. The rotating electrical machine system according to claim 1, wherein a first thread is formed on an outer surface of the inner shaft, the restraining member has a second screw that is threadedly engaged with the first screw and an accommodating hole in which the first outer shaft end is accommodated, and the restraining member and the first outer shaft end are spigot-fitted together by accommodating the first outer shaft end in the accommodating hole, a rotating electrical machine system in which the first inner shaft end and the first outer shaft end are spigot-fitted together;

5. 5. The rotating electric machine system according to claim 1, wherein the rotation parameter detector is a resolver having a resolver rotor and a resolver stator, and the resolver rotor is attached to the protruding tip.

6. 6. A rotating electric machine system according to claim 1, wherein a transmitting connector is provided on the holding member, and the transmitting connector electrically connects the rotation parameter detector to a receiver that receives a signal emitted by the rotation parameter detector.

7. A rotating electrical machine system according to any one of claims 1 to 6; an internal combustion engine having an output shaft that rotates integrally with the rotary shaft according to claim 1; Equipped with The output shaft is coupled to at least one of the second outer shaft end and the second inner shaft end.

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