Rotating electric machine system and combined power system equipped therewith

Abstract

To provide a rotary electric machine system that avoids a situation where both ends of a partition wall member stretched based on thermal expansion receive compressive stress from another member.SOLUTION: A rotary electric machine system has a rotor 34 and a stator 36. A partition wall member 410 is interposed between the rotor and the stator. The partition wall member forms a rotor chamber 22 and an in-housing oil passage 23 inside a rotary electric machine housing. Both apical surfaces 410a, 410b in an axial direction of the partition wall member are not in contact with any member. In other words, both apical surfaces are a non-constraint surface not constrained by another member.SELECTED DRAWING: Figure 6

Description

Technical Field

[0001] The present invention relates to a rotating electrical machine system. The present invention also relates to a composite power system in which a rotating electrical machine system and an internal combustion engine are integrally configured.

Background Art

[0002] A rotating electrical machine includes a rotor having a rotating shaft and a stator located on the outer periphery of the rotor. A permanent magnet is held on the rotating shaft. When the rotating shaft rotates, an alternating magnetic field is formed by the permanent magnet and an electromagnetic coil in the stator. As a result, an induced current is generated in the electromagnetic coil. That is, in this case, the rotating electrical machine functions as a generator.

[0003] When an induced current continuously occurs in the rotating electrical machine, the rotating electrical machine gets hot. Under such circumstances, the conversion efficiency between mechanical energy and electrical energy decreases. Also, the magnetic force of the electromagnetic coil decreases. Along with this, the output of the rotating electrical machine decreases. To avoid this, the rotating electrical machine may be cooled.

[0004] For example, in the technique described in Patent Document 1, the stator is cooled with cooling oil supplied into a rotating electrical machine housing. In this case, a sleeve portion is provided between the rotor and the stator. Inside the sleeve portion, a rotor chamber housing the rotor is formed. Outside the sleeve portion, a stator chamber housing the stator is formed. The cooling oil is supplied to the stator chamber to cool the stator. Note that the rotor is covered with a cover member. The space between the cover member and the sleeve portion is sealed with a seal member. By this seal, the entry of the cooling oil into the rotor chamber is prevented.

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

Summary of the Invention

[0006] In the configuration described in Patent Document 1, it is conceivable to position and fix the sleeve portion inside the rotating electric machine housing. In this case, for example, both ends of the sleeve portion in the axial direction are constrained by some member. That is, both ends of the sleeve portion in the axial direction become so-called fixed ends.

[0007] Incidentally, as mentioned above, rotating electric machines generate heat during continuous operation. This causes thermal expansion of the sleeve portion. Since both ends of the sleeve portion in the axial direction are fixed ends, compressive stress concentrates at these ends. Therefore, there is a concern that the sleeve portion may be damaged.

[0008] The present invention aims to solve the problems described above. [Means for solving the problem]

[0009] According to one embodiment of the present invention, a rotating electric machine system comprising a rotating electric machine having a rotor and a stator, and a rotating electric machine housing housing the rotating electric machine, wherein the rotor has a rotating shaft and a permanent magnet provided on the rotating shaft, and the rotating electric machine system comprises a first bearing and a second bearing interposed between the rotating electric machine housing and the rotating shaft, a cylindrical partition member interposed between the rotor and the stator in the diametrical direction of the rotating shaft, a rotor chamber formed radially inward of the partition member and housing the rotor, an internal housing oil passage formed radially outward of the partition member and housing the stator, a first sealing member that seals the space between the outer peripheral wall at the first axial end of the partition member and the rotating electric machine housing, and a sealing member that seals the space between the outer peripheral wall at the second axial end of the partition member and the rotating electric machine housing. A rotating electric machine system is provided, comprising a second sealing member and an oil circulation supply device for circulating and supplying lubricating oil to the first bearing, the second bearing and the oil passage inside the housing, wherein the oil circulation supply device has a first oil supply line, a second oil supply line, a first oil recovery line and a second oil recovery line, the oil circulation supply device supplies the lubricating oil to the first bearing and the second bearing via the first oil supply line and supplies the lubricating oil to the oil passage inside the housing via the second oil supply line, the oil circulation supply device recovers the lubricating oil supplied to the first bearing and the second bearing via the first oil recovery line and recovers the lubricating oil that has flowed through the oil passage inside the housing via the second oil recovery line, and at least one of the axial end faces of the partition member is a non-contact surface that does not contact any member.

[0010] According to another embodiment of the present invention, a combined power system is provided comprising the above-described rotating electric machine system and an internal combustion engine, wherein the internal combustion engine has an output shaft that rotates integrally with the rotating shaft of the rotating electric machine system. [Effects of the Invention]

[0011] In this invention, at least one of the two end faces of the partition member in the axial direction is a non-contact surface that does not come into contact with any other member. In other words, at least one of the two end faces is an unrestrained surface that is not constrained by any other member. Therefore, when the rotating electric machine heats up due to continuous operation, at least one end of the partition member can freely expand along the axial direction of the partition member based on thermal expansion.

[0012] Therefore, compressive stress is avoided at both ends of the bulkhead member, which has expanded due to thermal expansion, from other members. In other words, the concentration of compressive stress at both ends of the bulkhead member is avoided. This eliminates concerns about damage to the bulkhead member. [Brief explanation of the drawing]

[0013] [Figure 1] Figure 1 is a schematic overall perspective view of a combined power system according to an embodiment of the present invention. [Figure 2] Figure 2 is a schematic overall perspective view of the rotating electric machine system that constitutes the combined power system. [Figure 3] Figure 3 is a schematic side cross-sectional view of a rotating electric machine system. [Figure 4] Figure 4 is an enlarged view of the main part of Figure 3. [Figure 5] Figure 5 is a magnified view of a key part of Figure 3, but of a different location than that shown in Figure 4. [Figure 6] Figure 6 is a side cross-sectional view of the main parts showing the outer shaft that constitutes the rotating shaft and the members provided on the outer shaft. [Figure 7] Figure 7 is an enlarged side view of the main components of the rotating electric machine housing, showing the rotor, bulkhead members, and stator along the axial direction. [Figure 8] Figure 8 is a schematic diagram of a current converter installed in a rotating electric machine housing. [Figure 9] Figure 9 is a schematic perspective view of the second sub-housing that constitutes the rotating electric machine housing and the inner housing in the engine housing. [Figure 10]FIG. 10 is a schematic side cross-sectional view of a rotating electrical machine system in a phase different from the phase of FIG. 3. [Figure 11] FIG. 11 is a schematic side cross-sectional view of a rotating electrical machine system showing the flow direction of lubricating oil (second cooling oil) flowing through an oil passage in the housing. [Figure 12] FIG. 12 is a schematic system diagram schematically showing an example of a lubricating oil flow path in a rotating electrical machine system. [Figure 13] FIG. 13 is a schematic side cross-sectional view of a gas turbine engine constituting a compound power system. [Figure 14] FIG. 14 is an enlarged view of the main part of FIG. 13. [Figure 15] FIG. 15 is a schematic side cross-sectional view in the case where a compression pump provided outside is used as a gas supply device. [Figure 16] FIG. 16 is a schematic system diagram schematically showing another example of a lubricating oil flow path in a rotating electrical machine system. [Figure 17] FIG. 17 is a schematic side cross-sectional view of a rotating electrical machine system in the case where lubricating oil flows through an oil passage in the housing in a direction opposite to that of FIG. 11.

DETAILED DESCRIPTION OF THE INVENTION

[0014] Each of "left", "right", "lower", and "upper" in the following refers to the left, right, lower, and upper directions in FIGS. 3 to 5, FIGS. 13, and FIGS. 14 in particular. However, these directions are for convenience in simplifying the description and facilitating understanding. That is, the directions described in the specification are not necessarily the directions when the compound power system is actually used.

[0015] Figure 1 is a schematic overall perspective view of the combined power system 500 according to this embodiment. The combined power system 500 comprises a rotating electric machine system 10 and a gas turbine engine 200. The axis extending along the longitudinal direction (axial direction) passing through the diameter center of the rotating electric machine system 10 coincides with the axis extending along the longitudinal direction (axial direction) passing through the diameter center of the gas turbine engine 200. In other words, the rotating electric machine system 10 and the gas turbine engine 200 are arranged in parallel on the same axis.

[0016] Hereinafter, the left end in the axial direction of the rotating electric machine system 10 and the gas turbine engine 200 may be referred to as the first end. Similarly, the right end in the axial direction of the rotating electric machine system 10 and the gas turbine engine 200 may be referred to as the second end. That is, in the rotating electric machine system 10, the left end that is spaced away from the gas turbine engine 200 is the first end. In the rotating electric machine system 10, the right end that is close to the gas turbine engine 200 is the second end. Also, in the gas turbine engine 200, the left end that is close to the rotating electric machine system 10 is the first end. In the gas turbine engine 200, the right end that is spaced away 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 located at the second end of the rotating electric machine system 10. The rotating electric machine system 10 is located at the first end of the gas turbine engine 200.

[0017] The combined power system 500 is used as a propulsion power source in, for example, flying objects, ships, or automobiles. Suitable examples of flying objects include drones and multicopters. When mounted on a flying object, the combined power system 500 serves as a power drive source to rotate propellers, ducted fans, etc. When mounted on a ship, the combined power system 500 serves as a propeller rotation force generator. When mounted on an automobile, the combined power system 500 serves as a power drive source to rotate motors.

[0018] The combined power system 500 can also be used as a power source for auxiliary power in aircraft, ships, buildings, etc. Furthermore, the combined power system 500 can be used as a gas turbine power generation facility.

[0019] As will be described later, the gas turbine engine 200 is an internal combustion engine. Furthermore, the gas turbine engine 200 is a gas supply device that provides compressed air (gas).

[0020] First, let's describe the rotating electric machine system 10. Figure 2 is a schematic overall perspective view of the rotating electric machine system 10. Figure 3 is a schematic side cross-sectional view of the rotating electric machine system 10. This rotating electric machine system 10 comprises a rotating electric machine 12 (for example, a generator) and a rotating electric machine housing 14 that houses the rotating electric machine 12.

[0021] The rotating electric machine housing 14 comprises a main housing 16, a first sub-housing 18, and a second sub-housing 20. The main housing 16 has a substantially cylindrical shape, with both its first and second ends being open. 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.

[0022] The main housing 16 has thick side walls that extend along the left-right direction. The main housing 16 has a hollow interior. This hollow interior is divided into a rotor chamber 22 and a stator chamber 23 by a partition member 410, which will be described later. The rotor chamber 22 is a room formed on the inner circumference (inside) of the partition member 410. The rotor chamber 23 is a room formed on the outer circumference (outside) of the partition member 410.

[0023] A cooling jacket 24 is formed in a spiral shape inside the side wall of the main housing 16. A cooling medium flows through the cooling jacket 24. The cooling medium flows with the first end upstream and the second end downstream. In other words, the direction of flow of the cooling medium is the first direction from the first end to the second end. The cooling medium moves along the cooling jacket 24 in a spiral spiral. A specific example of the cooling medium is cooling water. In this case, the cooling jacket 24 is a water jacket.

[0024] On the outer surface (outer wall) of the side wall of the main housing 16, a first casing 26 and a second casing 28 are provided near the edge of the first end. The first casing 26 and the second casing 28 are parts of the main housing 16. That is, 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 measuring instrument casing.

[0025] As shown in Figure 11, a lower contact chamber 290 and an upper terminal chamber 291 are formed inside the first casing 26. The contact chamber 290 communicates with the stator chamber 23. An insertion opening 292 is formed in the contact chamber 290, which opens on the end face of the first casing 26 facing the first end. The insertion opening 292 is closed by a cover member 293.

[0026] A holding member for holding 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, the detector holding member will be referred to as the "resolver holder 30" hereafter. As will be described later, a cap cover 32 is connected to the resolver holder 30 via a screw.

[0027] The rotating electric machine 12 comprises a rotor 34 and a stator 36 surrounding the outer circumference of the rotor 34. The rotor 34 includes a rotating shaft 40. The partition member 410 is interposed between the rotor 34 and the stator 36 in the diametrical direction of the rotating shaft 40. Therefore, the rotor 34 is located on the inner circumference side of the partition member 410. In other words, the rotor 34 is housed in the rotor chamber 22. On the other hand, the stator 36 is located on the outer circumference side of the partition member 410. In other words, the stator 36 is housed in the stator chamber 23.

[0028] 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 Figure 4) and a right open end 442 (see Figure 5). The inner shaft 42 is inserted into the outer shaft 44 so as to be removable.

[0029] The inner shaft 42 is longer than the outer shaft 44. The inner shaft 42 has a cylindrical section 421, a left end 422 (see Figure 4), and a right end 423 (see Figure 5). The left end 422 is connected to the left of the cylindrical section 421. Therefore, the left end 422 is the end of the inner shaft 42 that is spaced away from the gas turbine engine 200 (the first end). The right end 423 is connected to the right of the cylindrical section 421. Therefore, the right end 423 is the end of the inner shaft 42 that is close to the gas turbine engine 200 (the second end). The diameter of the cylindrical section 421 is smaller than that of the left end 422 and the right end 423. Also, the diameter of the right end 423 is smaller than that of the left end 422.

[0030] A portion of the left end 422 is exposed from the left opening end 441 of the outer shaft 44. The portion exposed from the left opening end 441 is the protruding tip 46, which will be described later. In the illustrated example, the right end 423 of the inner shaft 42 and the right opening end 442 of the outer shaft 44 are flush. However, the right end 423 may be positioned slightly off-center from the right opening end 442 toward the second end.

[0031] As shown in detail in Figure 4, the left end 422 of the inner shaft 42 is provided with a first external threaded portion 48, a flange portion 50, a stopper portion 52, and a second external threaded portion 54 in that order from right to left. The outer diameters of the first external threaded portion 48, flange portion 50, stopper portion 52, and second external threaded portion 54 increase in this order. The outer diameter of the second external threaded portion 54 is larger than the inner diameter of the outer shaft 44. Therefore, the right end of the second external threaded portion 54 abuts against the edge of the left open end 441 of the outer shaft 44. Consequently, the portion of the inner shaft 42 to the left of the second external threaded portion 54 is not inserted into the outer shaft 44.

[0032] A resolver rotor 56 is mounted on the flange portion 50. A small cap nut 58 is screwed onto the first external thread portion 48. The right end of the resolver rotor 56 is positioned by the stopper portion 52. The left end of the resolver rotor 56 is pressed by the small cap nut 58. In this way, the resolver rotor 56 is positioned and fixed to the flange portion 50.

[0033] Furthermore, a large cap nut 60 is screwed onto the second external thread portion 54. The right end of the large cap nut 60 covers the outer peripheral wall of the left open end 441 of the outer shaft 44. As a result, the left end portion 422 of the inner shaft 42 is restrained by the left open end 441 of the outer shaft 44. Note that both the first external thread portion 48 and the second external thread portion 54 are so-called reverse threads. Therefore, the small cap nut 58 and the large cap nut 60 are rotated counterclockwise when screwed on. After screwing, it is preferable to deform a portion 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.

[0034] As shown in Figure 5, 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. A female threaded portion 64 is engraved on 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 connected to the inner shaft 42 by screwing it into the female threaded portion 64. The output shaft 204 holds the compressor wheel 222 and the turbine wheel 224 (see Figure 13).

[0035] Furthermore, 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 (left-right direction) of the rotating electric machine system 10.

[0036] As shown in detail in Figure 6, the outer shaft 44 has first shaft sections 44a to sixth shaft sections 44f in this order from the first end to the second end. The outer diameters (diameters) of the first shaft sections 44a to sixth shaft sections 44f differ from each other. Specifically, the outer diameter increases from the first shaft section 44a to the fifth shaft section 44e. That is, for example, the second shaft section 44b is larger in diameter than the first shaft section 44a and smaller in diameter than the third shaft section 44c. Similarly, the third shaft section 44c is larger in diameter than the second shaft section 44b and smaller in diameter than the fourth shaft section 44d. Thus, the outer shaft 44 changes from a small diameter section to a large diameter section from the first shaft section 44a to the fifth shaft section 44e. In contrast, the outer diameter of the sixth shaft section 44f is smaller than the outer diameters of the third shaft section 44c to the fifth shaft section 44e.

[0037] A first stage 330 is formed between the first shaft portion 44a and the second shaft portion 44b based on the difference in outer diameter (diameter difference) between the two shaft portions 44a and 44b. A second stage 332 is formed between the second shaft portion 44b and the third shaft portion 44c based on the difference in outer diameter between the two shaft portions 44b and 44c. A third stage 334 is formed between the third shaft portion 44c and the fourth shaft portion 44d based on the difference in outer diameter between the two shaft portions 44c and 44d. A fourth stage 336 is formed between the fourth shaft portion 44d and the fifth shaft portion 44e based on the difference in outer diameter between the two shaft portions 44d and 44e.

[0038] Figure 7 is a side cross-sectional view of the vicinity of the left open end 441 of the outer shaft 44, viewed along the axial direction. As shown in Figure 7, an oil receiving recess 340 is formed near the first end of the first shaft portion 44a. The oil receiving recess 340 is an annular recess formed on the outer surface of the first shaft portion 44a.

[0039] The rotating shaft 40 has an oil guide member 350 which is an annular shape. Specifically, the oil guide member 350 is positioned and fixed to the outer circumferential wall of the first shaft portion 44a. That is, the first shaft portion 44a has a first threaded portion 348, and the oil guide member 350 has a second threaded portion 352 (see Figure 7). The oil guide member 350 is positioned and fixed to the first shaft portion 44a by screwing the second threaded portion 352 into the first threaded portion 348.

[0040] The oil guide member 350 is positioned facing the oil receiving recess 340 formed in the rotating shaft 40 (the first shaft portion 44a of the outer shaft 44). An annular gap 385 for receiving lubricating oil is formed between the opening of the oil guide member 350 and the oil receiving recess 340. The annular gap 385 is the inlet to the rotor internal oil passage 354. The outlet of the rotor internal oil passage 354 is an opening facing the second end of the hole in the second magnet stopper 358.

[0041] Multiple first oil supply passages 386 are formed in the oil guide member 350. The first oil supply passages 386 extend along the axial direction of the rotating shaft 40 (see Figure 7). The outlets of the multiple first oil supply passages 386 are connected to the flow space 374, which is part of the rotor internal oil passage 354. In other words, the first oil supply passages 386 communicate with the rotor internal oil passage 354.

[0042] Multiple upstream guide grooves 390 (first guide grooves) are formed on the outer circumferential wall of the oil guide member 350. Two adjacent upstream guide grooves 390 are spaced, for example, 60° apart.

[0043] A first outer stopper 81, which is one of the bearing stoppers, is provided at the second end of the first shaft portion 44a. A first inner stopper 82, which is another bearing stopper, is provided at the second shaft portion 44b. A first bearing 74 is sandwiched between the first outer stopper 81 and the first inner stopper 82.

[0044] As shown in Figure 6, permanent magnets 72 are held in the third shaft portion 44c to the fifth shaft portion 44e via a cylindrical member 70. The rotor 34 is composed of a rotating shaft 40, a cylindrical member 70, and permanent magnets 72. An inner hole 73 is formed in the cylindrical member 70, extending along the axial direction of the cylindrical member 70. The rotating shaft 40 passes through the inner hole 73. Therefore, the cylindrical member 70 is interposed between the rotating shaft 40 and the permanent magnets 72 in the diametrical direction of the rotating shaft 40. In the inner hole 73, the inner diameter is larger in the portion corresponding to the third stage portion 334.

[0045] The cylindrical member 70 and the permanent magnet 72 are sandwiched between the first magnet stopper 356 and the second magnet stopper 358 in the axial direction of the rotating shaft 40. This positions the cylindrical member 70 within the third shaft portion 44c to the fifth shaft portion 44e. In other words, misalignment of the cylindrical member 70 and the permanent magnet 72 from the third shaft portion 44c to the fifth shaft portion 44e is prevented. In this way, the first magnet stopper 356 and the second magnet stopper 358 position the permanent magnet 72.

[0046] The first magnet stopper 356 straddles the second end of the second shaft portion 44b and the first end of the third shaft portion 44c. The second magnet stopper 358 covers the outer surface of the fifth shaft portion 44e. A first ring body 363 is sandwiched between the first magnet stopper 356 and the permanent magnet 72. Similarly, a second ring body 364 is sandwiched between the permanent magnet 72 and the second magnet stopper 358. The first and second ends of the cylindrical member 70 are passed through the through holes of the first ring body 363 and the second ring body 364, respectively.

[0047] An inward projection 3581 is provided on the inner circumferential wall of the hole in the second magnet stopper 358. The inward projection 3581 protrudes in an annular shape toward the diametrically inward direction of the hole. The inner circumferential wall of the inward projection 3581 abuts against the top surface of the fourth stage 336. Multiple second oil supply passages 3582 are formed in the inward projection 3581. The multiple second oil supply passages 3582 are arranged along the circumferential direction of the inward projection 3581. One of the second oil supply passages 3582 extends along the axial direction of the rotating shaft 40.

[0048] As shown in Figure 3, the left end (first end) of the rotating shaft 40 is rotatably supported by the first sub-housing 18 via a first bearing 74. 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 projection 76 that protrudes toward the main housing 16, as shown in Figures 3 and 7. A first insertion hole 78 is formed in the cylindrical projection 76. A first bearing holder 80, which holds the first bearing 74, is inserted into the first insertion hole 78. Thus, the first bearing 74 is positioned in the first insertion hole 78.

[0049] The first insertion hole 78 extends along the left-right direction. The left end of the first insertion hole 78 is further away 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".

[0050] As shown in Figure 7, a first outer stopper 81 is provided at the first end of the first shaft portion 44a. The first outer stopper 81 is an annular shape, and a plurality of downstream guide grooves 368 (second guide grooves) are formed on its outer circumferential wall. It is preferable that the phases of the upstream guide groove 390 and the downstream guide groove 368 coincide, but it is not necessary for them to coincide.

[0051] A first internal stopper 82 is provided on the second shaft portion 44b. The first internal stopper 82 has a small diameter cylindrical portion 370 with a small outer diameter and a large diameter cylindrical portion 372 with a large outer diameter. The first internal stopper 82 covers the outer surface of the second shaft portion 44b such that the small diameter cylindrical portion 370 faces the first end and the large diameter cylindrical portion 372 faces the second end.

[0052] As described above, an annular flow space 374 is formed between the first shaft portion 44a and the second shaft portion 44b and the inner circumferential wall of the first inner stopper 82. An annular flow space 360 ​​is also formed between the outer surfaces of the second shaft portion 44b and the third shaft portion 44c and the inner circumferential wall of the hole in the first magnet stopper 356. An annular flow space 353 is also formed between the outer surfaces of the third shaft portion 44c to the fifth shaft portion 44e and the inner wall of the inner hole 73 of the cylindrical member 70. An annular flow space 362 is also formed between the outer surface of the sixth shaft portion 44f and the inner circumferential wall of the hole in the second magnet stopper 358. The flow spaces 374, 360, 353, and 362 are connected to form the rotor internal oil passage 354. The flow space 353 and the flow space 362 are connected via the second oil supply passage 3582.

[0053] The rotor oil passage 354 is a flow path extending along the axial direction of the rotating shaft 40, and may be, for example, a partially annular space in the axial direction. The rotor oil passage 354 extends from the first end to the second end of the permanent magnet 72 in the axial direction of the rotating shaft 40. The rotor oil passage 354 may be a groove or the like.

[0054] The end face of the second end of the oil guide member 350 abuts against the end face of the first end of the small diameter cylindrical portion 370. The end face of the first end of the first magnet stopper 356 abuts against the end face of the second end of the large diameter cylindrical portion 372. In addition, the first outer stopper 81 is positioned and fixed to the outer peripheral wall of the first end of the small diameter cylindrical portion 370. The first bearing 74 is arranged on the outer circumference of the small diameter cylindrical portion 370 and is sandwiched between the end face of the second end of the first outer stopper 81 and the end face of the first end of the large diameter cylindrical portion 372.

[0055] The tip of the left end of the rotating shaft 40 passes through the inner bore of the first bearing 74 and then through the first insertion hole 78. The tip of the left end of the rotating shaft 40 is further exposed to the outside of the cylindrical projection 76 (hollow recess 118). Hereinafter, the portion of the rotating shaft 40 that protrudes from the left end of the first bearing 74 will be referred to as the "protruding tip 46". The protruding tip 46 includes the first external thread portion 48, the flange portion 50, the stopper portion 52, and the second external thread portion 54 of the left end 422 of the inner shaft 42 (see Figure 4).

[0056] A second bearing 84 is provided on the sixth shaft portion 44f of the outer shaft 44. The second bearing 84 rotatably supports the right end (second end) of the rotating shaft 40 in the second sub-housing 20. As shown in Figure 5, the second bearing 84 is inserted between the outer shaft 44 and the second sub-housing 20, which has a roughly disc shape.

[0057] 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 this cylindrical portion. The second insertion hole 86 extends along the left-right direction. The left end of the second insertion hole 86 is further away 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). Hereinafter, the right end of the second insertion hole 86 will also be referred to as the "second proximal end 862".

[0058] A second bearing holder 88, which holds the second bearing 84, is inserted into the second insertion hole 86. Thus, the second bearing 84 is positioned in the second insertion hole 86. The second bearing 84 is held 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 holding, the second bearing 84 is positioned and fixed to the sixth shaft portion 44f. In this way, the second inner stopper 90 and the second outer stopper 92 are bearing stoppers.

[0059] The rotor 34 has a disc portion 392 as shown in Figure 6. The disc portion 392 is provided at the first end of the second inner stopper 90 and is a projection that protrudes radially outward from the rotating shaft 40 on the outer circumference of the rotating shaft 40. The disc portion 392 is located between the permanent magnet 72 and the second bearing 84 in the axial direction of the rotating shaft 40 and partially covers the opening 358a of the hole in the second magnet stopper 358. In other words, the disc portion 392 is a shielding portion provided at the outlet of the flow space 362 (outlet of the rotor internal oil passage 354). The disc portion 392 is located inward (towards the first end) from the second bearing 84.

[0060] The disc portion 392 faces the second bearing 84 in the axial direction of the rotating shaft 40. Because the disc portion 392 partially shields the outlet of the flow space 362, the lubricating oil that has come into contact with the second bearing 84 is separated from the lubricating oil that has flowed out from the rotor's internal oil passage 354.

[0061] Furthermore, at the second distal end 861, a clearance is formed between the second internal stopper 90 and the second bearing holder 88. This clearance is the third sub-branch 941.

[0062] As shown in Figures 2 and 3, a flow straightening member 96 is connected to the end face of the second sub-housing 20 facing the gas turbine engine 200. The flow straightening member 96 has a base portion 98, a reduced diameter portion 100, and a top portion 102. The base portion 98 facing the second sub-housing 20 is a large-diameter, thin-walled cylindrical plate. The top portion 102 facing the gas turbine engine 200 is a small-diameter, relatively long cylindrical plate. In the reduced diameter portion 100 between the base portion 98 and the top portion 102, the diameter gradually decreases. Therefore, the flow straightening member 96 is a V-shaped or bottomless cup-shaped body. The outer surface of the reduced diameter portion 100 is a smooth surface with low surface roughness.

[0063] At the base portion 98, an inlet 104 is formed on the end face 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 the input port for compressed air to the relay chamber 106.

[0064] An insertion hole 108 is formed in the top portion 102, extending in 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 rotating shaft 40. Therefore, the portion of the second outer stopper 92 that enters the insertion hole 108 and its 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 fourth sub-branch 942. The relay chamber 106 widens as it approaches the insertion hole 108 and the fourth sub-branch 942.

[0065] Furthermore, the diameter (opening diameter) of the through hole 108 is larger than the outer diameter of the relatively small left end (small diameter cylindrical portion 242) of the compressor wheel 222. Therefore, the small diameter cylindrical portion 242 that enters the through hole 108 is also spaced apart from the inner wall of the through hole 108. In other words, a clearance is formed between the outer circumferential wall of the small diameter cylindrical portion 242 and the inner wall of the through hole 108. This clearance is the outlet passage 943.

[0066] As shown in Figure 3, the first insertion hole 78 and the third sub-branch 941 communicate with the rotor chamber 22.

[0067] The stator 36, together with the rotor 34 described above, constitutes the rotating electric machine 12. The stator 36 has an electromagnetic coil 110 and a plurality of insulating base materials 112. The electromagnetic coil 110 has three types: U-phase coil, V-phase coil, and W-phase coil, and is wound around the insulating base materials 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 base materials 112 are arranged in a ring shape. This arrangement forms an internal hole in the stator 36. A cylindrical projection 76 enters the left opening of the internal hole of the stator 36.

[0068] As described above, a partition member 410 is interposed between the rotor 34 and the stator 36. As can be seen from Figure 6, the partition member 410 is cylindrical. Therefore, the partition member 410 surrounds most of the rotor 34 from the outer circumference. This forms a rotor chamber 22 inside the partition member 410. The rotor 34 is housed in this rotor chamber 22.

[0069] As will be described later, compressed air, which is a gas, flows through the rotor chamber 22. Here, a clearance is formed between the outer circumferential wall of the cylindrical projection 76 and the insulating substrate 112. The compressed air flows through this clearance. In other words, this clearance is part of the compressed air path inside the rotating electric machine housing 14.

[0070] The first sub-housing 18 has three intake passages 450 formed therein to supply compressed air to the rotor chamber 22. Figure 3 shows one of the three intake passages 450.

[0071] One of the intake passages 450 is inclined from the diametrically outward to the diametrically inward direction of the first sub-housing 18 as it moves from the first end to the second end of the first sub-housing 18. The first end of the intake passage 450 opens at the end face of the first sub-housing 18 facing the first end. This opening is the inlet for compressed air into the rotating electric machine housing 14. The second end of the intake passage 450 opens facing the first end of the partition member 410. This opening is the inlet for compressed air into the rotor chamber 22.

[0072] A portion of the compressed air flows from the starting path 450 towards the first bearing 74. The remaining portion of the compressed air flows from the starting path 450 through the rotor chamber 22 towards the second bearing 84. Thus, the direction of flow of compressed air in the rotor chamber 22 is the first direction, from the first end to the second end.

[0073] The tip of the second end of the cylindrical projection 76 enters the space between the inner bore of the stator 36 and the outer peripheral wall at the first end of the partition member 410. A first sealing member 453 is provided at the tip of the second end of the cylindrical projection 76. The first sealing member 453 is an O-ring and seals the space between the tip of the second end of the cylindrical projection 76 and the outer peripheral wall at the first end of the partition member 410. As shown in Figures 4 and 6, the first sub-housing 18 and the like do not come into contact with the tip surface 410a at the first end of the partition member 410.

[0074] On the other hand, a space is formed between the outer periphery wall of the partition member 410 and the main housing 16. This space is the stator chamber 23. The stator 36 is housed in the stator chamber 23. The inner wall of the stator chamber 23 and the electromagnetic coil 110 are slightly separated from each other. That is, a clearance is formed between the inner wall of the stator chamber 23 and the electromagnetic coil 110. This clearance electrically insulates the main housing 16 from the electromagnetic coil 110.

[0075] As will be described later, lubricating oil flows through the stator chamber 23. In other words, the stator chamber 23 is part of the internal oil passage formed inside the rotating electric machine housing 14. Here, a clearance is also formed between the outer peripheral wall of the partition member 410 and the electromagnetic coil 110. This clearance is also part of the oil passage. Hereafter, this oil passage will be referred to as the "stator inner circumference oil passage 454". The lubricating oil flowing through the stator chamber 23 (internal housing oil passage) and the stator inner circumference oil passage 454 is a separate flow from the lubricating oil supplied to the first bearing 74 and the second bearing 84.

[0076] In the second sub-housing 20, an inner annular projection 456 and an outer annular projection 458 are provided concentrically on the surface facing the first end. The inner annular projection 456 is located on the inner circumference of the outer annular projection 458. An annular recess 114 is formed between the inner annular projection 456 and the outer annular projection 458. An insulating substrate 112 constituting the stator 36 is inserted into the annular recess 114.

[0077] The internal annular projection 456 is passed through the through hole of the annular holder 460. The second end of the annular holder 460 is flanged and expands in diameter, and abuts against the end face of the first end of the annular recess 114.

[0078] The first end of the annular holder 460 extends toward the partition member 410. At the first end of the annular holder 460, a second sealing member 464 is provided on the inner surface facing the outer peripheral wall of the partition member 410. The second sealing member 464 is an O-ring and seals the space between the inner peripheral wall at the first end of the annular holder 460 and the outer peripheral wall at the second end of the partition member 410.

[0079] An annular guide 466 is interposed between the inner annular projection 456 and the inner circumferential wall at the second end of the partition member 410. The first end of the annular guide 466 is a tapered portion 467 that tapers in diameter towards the second end. A third sealing member 468 is provided on the outer surface of the annular guide 466 that faces the inner circumferential wall of the partition member 410. The third sealing member 468 is an O-ring and seals the space between the outer circumferential wall of the annular guide 466 and the inner circumferential wall at the second end of the partition member 410. As shown in Figures 5 and 6, the second sub-housing 20 and the like do not come into contact with the tip surface 410b at the second end of the partition member 410.

[0080] The first sealing member 453, the second sealing member 464, and the third sealing member 468 create independent spaces for the rotor chamber 22 and the stator chamber 23. This prevents, for example, the compressed air supplied to the rotor chamber 22 from leaking into the stator chamber 23. It also prevents the lubricating oil supplied to the stator chamber 23 from leaking into the rotor chamber 22.

[0081] The outer peripheral wall at the first end of the partition member 410 contacts the first sub-housing 18 via the first sealing member 453. The second end of the partition member 410 is sandwiched between the annular guide 466 and the annular holder 460 via the second sealing member 464 and the third sealing member 468. The partition member 410 does not particularly abut against any other members. Furthermore, there are no members that abut the tip surface 410a of the first end and the tip surface 410b of the second end of the partition member 410. As can be understood from this, the axial tip surfaces 410a and 410b of the partition member 410 are unrestrained surfaces that are not constrained by any other members. Therefore, both ends of the partition member 410 can undergo thermal expansion freely in the axial direction of the partition member 410.

[0082] In this embodiment, both end surfaces 410a and 410b are unrestrained surfaces, but some member may be in contact with either end surface 410a or end surface 410b.

[0083] If the thickness T of the partition member 410 shown in Figure 7 is large, the weight of the partition member 410 increases, and the rotating electric machine 12 becomes larger in the diametrical direction. In addition, a partition member 410 with a large thickness T blocks the alternating magnetic field between the permanent magnet 72 and the electromagnetic coil 110. To avoid the above problems, it is preferable that the thickness T be as small as possible. For example, the thickness T is preferably around 1 mm.

[0084] Therefore, it is preferable that the partition member 410 be made of a material that has sufficient strength and rigidity even if it is thin. A suitable example of such a material is ceramics. In order to avoid the alternating magnetic field between the rotor 34 and the stator 36 being blocked, insulating and non-magnetic ceramics are particularly preferred. Specific examples include aluminum nitride (AlN), silicon nitride (Si3N4), and alumina (Al2O3). Of these, alumina is particularly preferred because it is inexpensive.

[0085] As shown in Figure 7, the distance between the permanent magnets 72 constituting the rotor 34 and the inner circumferential wall of the partition member 410 is defined as the inner separation distance Din. The distance between the outer circumferential wall of the partition member 410 and the electromagnetic coils 110 constituting the stator 36 is defined as the outer separation distance Dout. If the inner separation distance Din is smaller than the outer separation distance Dout, turbulence is more likely to occur in the compressed air flowing between the permanent magnets 72 and the partition member 410, resulting in greater windage losses. Furthermore, the frictional resistance between the rotor 34 and the compressed air increases, leading to greater frictional heat generated in the permanent magnets 72.

[0086] To avoid the problems described above, in this embodiment, the inner separation distance Din is set to be greater than the outer separation distance Dout. That is, the following relationship holds. Din>Dout

[0087] It is preferable that Din is 2.5 times or more Dout. It is also possible to set Din to 6 times or more Dout, but if Din is excessively large, the rotating electric machine 12 will become excessively large in the diametrical direction. If the sum of Din and Dout is kept constant and Din is made excessively large to avoid this, Dout will become excessively small, making it difficult for the lubricating oil to flow through the oil passage 454 on the inner circumference side of the stator. Therefore, it is preferable to set Din to approximately 3.5 to approximately 4 times Dout. An example of a combination of Din and Dout is that Din is in the range of 1.1 mm to 2.1 mm and Dout is in the range of 0.3 mm to 0.5 mm.

[0088] As shown in Figure 4, the first sub-housing 18 has an annular projection 116 that protrudes in a ring shape. The inside of the annular projection 116 is a hollow recess 118. The protruding tip 46, which is part of the left end 422 of the inner shaft 42, enters the hollow recess 118.

[0089] A resolver holder 30 is provided on the annular projection 116. The resolver holder 30 has a flange-shaped stopper 120 that protrudes diametrically outward. The flange-shaped stopper 120 has a larger diameter than the inner diameter of the annular projection 116. Therefore, the flange-shaped stopper 120 abuts against the annular projection 116. This abutment positions the resolver holder 30. In this state, the resolver holder 30 is connected to the first sub-housing 18, for example, via mounting bolts (not shown).

[0090] In the resolver holder 30, a small cylindrical portion 122 is provided to the left of the flange-shaped stopper 120. 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. This fitting holds the resolver stator 130 in the resolver holder 30.

[0091] When the large cylindrical portion 124 enters the hollow recess 118 and the flange-shaped stopper 120 contacts the annular protrusion 116, the resolver rotor 56 is positioned in the inner bore of the resolver stator 130. The resolver stator 130 and the resolver rotor 56 constitute the 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 portion 50 of the left end portion 422 of the inner shaft 42.

[0092] An engagement hole 134 is formed in the flange-shaped stopper 120. The 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. The 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.

[0093] Multiple tab portions 140 are provided on the small cylindrical portion 122 (omitted in Figure 1). Figure 3 shows one tab portion 140. 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 connecting bolts 142.

[0094] As described above, a first casing 26 and a second casing 28 are integrally provided on the side wall near the left end of the main housing 16. The terminal chamber 291 of the first casing 26 houses a U-phase terminal 1441, a V-phase terminal 1442, and a 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, V-phase terminal 1442, and W-phase terminal 1443 are electrical terminals to which external equipment (external load or external power supply) is electrically connected. The power generated by the rotating electric machine 12 is supplied to the external equipment. An example of an external load is a motor (not shown). Another example of external equipment is the battery 146 shown in Figure 8.

[0095] The electrical contact between the U-phase terminal 1441 and the U-phase coil is provided in the contact chamber 290 of the first casing 26. Similarly, the electrical contact between the V-phase terminal 1442 and the V-phase coil is also provided in the contact chamber 290. Similarly, the electrical contact between the W-phase terminal 1443 and the W-phase coil is also provided in the contact chamber 290. To illustrate the electrical contact between the V-phase terminal 1442 and the V-phase coil, as shown in Figure 11, the V-phase terminal 1442 has a closing projection 294. The closing projection 294 closes the communication opening between the contact chamber 290 and the terminal chamber 291. This closure makes the contact chamber 290 and the terminal chamber 291 independent spaces from each other.

[0096] The terminal portion 295 of the V-phase terminal 1442 is provided on the blocking projection 294. The terminal portion 295 extends into the contact chamber 290. Also, the terminal wire 110a, which is the end of the V-phase coil, is led out into the contact chamber 290. Within the contact chamber 290, the terminal portion 295 and the terminal wire 110a are connected via a screw 296. This electrically connects the V-phase terminal 1442 and the V-phase coil. Although not specifically shown, the U-phase terminal 1441 and the U-phase coil are similarly connected within the contact chamber 290. The W-phase terminal 1443 and the W-phase coil are similarly connected within the contact chamber 290.

[0097] The second casing 28 is adjacent to the first casing 26. The second casing 28 houses a thermistor 148, which is a temperature measuring instrument. Although not specifically shown in the diagram, the measuring terminals of the thermistor 148 are led out from the second casing 28 and connected to the electromagnetic coil 110. A harness 149 connected to the thermistor 148 is led out from the second casing 28 to the outside.

[0098] As shown in Figures 1 and 2, a current converter 150 is provided on the outer periphery wall of the main housing 16. The current converter 150 is positioned closer to the gas turbine engine 200 than the first casing 26. As shown in Figure 8, the current converter 150 includes a conversion circuit 152, a capacitor 154, and a control circuit 156. These conversion circuit 152, capacitor 154, and control circuit 156 are housed in an equipment case 158. The equipment case 158 is positioned, for example, on the outer periphery wall of the main housing 16, in a location that does not interfere with the first hollow tube section 1601, the second hollow tube section 1602, and the third hollow tube section 1603 (see Figure 1).

[0099] The hollow interiors of the first hollow tube section 1601, the second hollow tube section 1602, and the third hollow tube section 1603 are compressed air passages through which compressed air flows. In other words, in this embodiment, three compressed air passages are formed in the rotating electric machine housing 14. The first hollow tube section 1601 and the third hollow tube section 1603 are formed, for example, as hollow bulges that protrude from the outer peripheral wall of the main housing 16.

[0100] In the first sub-housing 18, the end face facing the first end has openings at the first ends of three starting passages 450. One of the openings of the three starting passages 450 is connected to the first hollow pipe section 1601 via a flexible tube 470a. Another opening of the three starting passages 450 is connected to the second hollow pipe section 1602 via a flexible tube 470b. Yet another opening of the three starting passages 450 is connected to the third hollow pipe section 1603 via a flexible tube 470c.

[0101] The conversion circuit 152 includes a power module 161. The conversion circuit 152 converts the alternating current generated in the electromagnetic coil 110 into a direct current. At this time, the capacitor 154 temporarily stores the direct current converted by the conversion circuit 152 as an electric charge. The conversion circuit 152 also has the function of converting the direct current supplied from the battery 146 into an alternating current. In this case, the capacitor 154 temporarily stores the direct current supplied from the battery 146 to the electromagnetic coil 110 as an electric charge.

[0102] The control circuit 156 controls the current density of the DC current flowing from the capacitor 154 to the battery 146, or in the reverse direction. The DC current from the battery 146 is supplied to a motor (not shown) via, for example, an AC-to-DC converter.

[0103] The rotating electric machine system 10, configured as described above, is provided with a compressed air passage and a lubricating oil passage (a first oil supply passage and a second oil supply passage). First, the compressed air passage will be described.

[0104] As shown in Figure 9, in the second sub-housing 20, an annular manifold passage 162 consisting of an annular recess is formed on the end face facing the gas turbine engine 200. As will be described later, a portion of the compressed air generated by the gas turbine engine 200 flows through the manifold passage 162. Three upstream communication holes 164 are formed in the bottom wall of the manifold passage 162 (annular recess). The upstream communication holes 164 are input ports for compressed air.

[0105] An air relay passage 166, which serves as a gas branching passage, is provided inside the second sub-housing 20. The air relay passage 166 extends radially along the diametrical direction of the second sub-housing 20. The air relay passage 166 communicates with the manifold passage 162 via an upstream communication hole 164 in the diametrically outward direction. In addition, three first downstream communication holes 1681 to 1683 are formed on the end face of the second sub-housing 20 facing the rotating electric machine 12. The first downstream communication holes 1681 to 1683 are the first output ports of the air relay passage 166. A distribution passage is formed by the manifold passage 162 and the air relay passage 166.

[0106] In the second sub-housing 20, three second downstream communication holes 1701 to 1703 are formed on the end face facing the gas turbine engine 200. The second downstream communication holes 1701 to 1703 are the second output ports of the air relay path 166. The second downstream communication holes 1701 to 1703 are located diametrically inward from the first downstream communication holes 1681 to 1683. Therefore, the compressed air flowing through the air relay path 166 is divided into compressed air entering the first downstream communication holes 1681 to 1683 (first branch airflow) and compressed air entering the second downstream communication holes 1701 to 1703 (second branch airflow). In this way, the air relay path 166 functions as a branching path.

[0107] As shown in Figure 2, the outer surface of the side wall of the main housing 16 is provided with a first hollow tube section 1601, a second hollow tube section 1602, and a third hollow tube section 1603. The first downstream communication holes 1681 to 1683 each open individually toward the first hollow tube section 1601 to the third hollow tube section 1603. As can be seen from this, the air relay path 166 connects the collective flow path 162 with the hollow interiors of the first hollow tube section 1601 to the third hollow tube section 1603. As shown in Figure 3, the first hollow tube section 1601 to the third hollow tube section 1603 are located diametrically outward from the cooling jacket 24 formed inside the side wall of the main housing 16.

[0108] The first to third hollow tube sections 1601 to 1603 extend along the axial direction of the main housing 16. That is, the first to third hollow tube sections 1601 to 1603 extend from the second end facing the gas turbine engine 200 toward the first casing 26 (or first end). As described above, the first to third hollow tube sections 1601 to 1603 are each connected to three starting passages 450 via flexible tubes 470a to 470c. Therefore, compressed air flowing through the first to third hollow tube sections 1601 to 1603 flows into the starting passages 450 via flexible tubes 470a to 470c. As can be understood from this, the first to third hollow tube sections 1601 to 1603 are gas supply passages that supply compressed air.

[0109] In this embodiment, the case in which the first hollow tube section 1601 to the third hollow tube section 1603 are provided is illustrated, but the number of hollow tube sections is appropriately determined according to the flow rate or velocity required for the curtain air formed from compressed air. In other words, the number of hollow tube sections is not limited to three. Similarly, the cross-sectional area of ​​the hollow tube sections is also appropriately determined according to the flow rate or velocity required for the curtain air.

[0110] The compressed air that flows into the starting path 450 then splits into compressed air that goes towards the first insertion hole 78 and compressed air that goes towards 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 heads towards the first insertion hole 78. Thus, the clearance between the first sub-housing 18 and the rotor 34 is the first air branching path L. On the other hand, the remaining portion of the compressed air mainly flows through the clearance between the outer wall of the permanent magnet 72 and the inner wall of the electromagnetic coil 110 and heads towards the second insertion hole 86. Thus, the clearance between the outer wall of the permanent magnet 72 and the inner wall of the electromagnetic coil 110 is the second air branching path M.

[0111] The compressed air that reaches the first air branch L forms an air curtain that seals the lubricating oil supplied to the first bearing 74. Similarly, the compressed air that reaches the third sub-branch 941 (the second distal end 861 of the second insertion hole 86) from the second air branch M also forms an air curtain that seals the lubricating oil supplied to the second bearing 84. Thus, the compressed air flowing through the starting passage 450 functions as a curtain air.

[0112] As shown in Figure 5, three inlets 104 are formed in the base portion 98 of the rectifier member 96. One of them is shown in Figure 5. One inlet 104 is connected to the second downstream communication hole 1701 (not shown). Another inlet 104 is connected to the second downstream communication hole 1702 (shown). Yet another inlet 104 is connected to the second downstream communication hole 1703 (not shown). Therefore, compressed air output from the second downstream communication holes 1701 to 1703 enters the relay chamber 106 of the reduced diameter portion 100 of the rectifier member 96 via the inlets 104.

[0113] The relay chamber 106 is connected to the through hole 108 formed in the top portion 102. Here, the relay chamber 106 widens as it approaches the through hole 108 and the fourth sub-branch 942. As a result, the pressure of the curtain air decreases as the compressed air flows through the relay chamber 106.

[0114] The outlet of the relay chamber 106 faces the small-diameter cylindrical portion 242 of the compressor wheel 222. Therefore, the compressed air entering the relay chamber 106 comes into contact with the small-diameter cylindrical portion 242 of the compressor wheel 222. The compressed air then splits into compressed air heading toward the fourth sub-branch 942 and compressed air heading toward the outlet 943. As a result, the pressure of the compressed air heading toward the second proximal end 862 of the second insertion hole 86 along the fourth sub-branch 942 decreases.

[0115] The compressed air that reaches the second proximal end 862 of the second insertion hole 86 from the fourth sub-branch passage 942 forms an air curtain that seals the lubricating oil supplied to the second bearing 84. The compressed air that flows into the outlet passage 943 is led inward to the first end (open end) of the shroud case 220. This compressed air is then drawn back into the compressor wheel 222.

[0116] As shown in Figure 3, an exhaust passage 172 (gas discharge passage) is formed in the main housing 16. Compressed air that reaches the first air branch passage L and compressed air that reaches the second air branch passage M are exhausted to the outside of the main housing 16 via the exhaust passage 172.

[0117] Next, the lubrication oil flow path will be described. Figures 10 and 11 are schematic side cross-sectional views of the rotating electric machine system 10. Note that Figure 10 shows a different phase than that shown in Figure 3. The rotating electric machine housing 14 has a lubrication oil flow path formed therein, which includes a first oil supply path, a first oil recovery path, a second oil supply path, and a second oil recovery path.

[0118] The first oil supply passage includes an input passage 174, a main oil passage 176, a first secondary oil passage 180, and a second secondary oil passage 181. Of these, the input passage 174 is formed at a position closer to the first end than the axial midpoint of the main housing 16. The input passage 174 extends along the diametrical direction of the main housing 16 and communicates with the main oil passage 176. The main oil passage 176 is formed on the outer circumference of the cooling jacket 24 and extends along the axial direction of the main housing 16. The main oil passage 176 branches at the point where it communicates with the input passage 174 into a first oil branch passage N leading to the first sub-housing 18 and a second oil branch passage R leading to the second sub-housing 20.

[0119] In the first sub-housing 18, a first inlet hole 178 is formed at the location facing the first oil branch passage N. Furthermore, a first secondary oil passage 180 is formed inside the first sub-housing 18, extending diametrically inward. The first secondary oil passage 180 bends at two points before reaching the first bearing holder 80.

[0120] A second secondary oil passage 181 branches off from the first secondary oil passage 180. Here, as shown in Figures 7 and 10, the first sub-housing 18 has a protruding end 400 that projects toward the oil guide member 350. The tip of the second secondary oil passage 181 extends into the interior of the protruding end 400. The outlet of the second secondary oil passage 181 is slightly bent. The outlet of the second secondary oil passage 181 discharges lubricating oil toward the annular gap 385 of the rotor 34.

[0121] The first bearing holder 80 has a first oil supply hole 182 that communicates with the first secondary oil passage 180. The outlet of the first oil supply hole 182 is formed at the first distal end 781 of the first insertion hole 78. Therefore, the lubricating oil that flows from the main oil passage 176 into the first secondary oil passage 180 flows from the first oil supply hole 182 to the first distal end 781 of the first insertion hole 78 and comes into contact with the first bearing 74.

[0122] As shown in Figure 3, the first sub-housing 18 has a first drain passage 184 which is part of the first oil recovery passage. The first drain passage 184 discharges the lubricating oil that has come into contact with the first bearing 74 from a hollow recess 118 formed by the annular protrusion 116 of the first sub-housing 18 and the resolver holder 30. The lubricating oil discharged from the first drain passage 184 is recovered in the gas-liquid separator 302 (described later). Thus, the first drain passage 184 also serves as the first oil conduit that guides the lubricating oil to the gas-liquid separator 302.

[0123] Three of each of the first oil branch passage N, first inlet 178, first secondary oil passage 180, and first oil supply hole 182 are formed. Similarly, three of the second oil branch passage R are formed. Figure 10 shows one of each of the first oil branch passage N, first inlet 178, first secondary oil passage 180, first oil supply hole 182, and second oil branch passage R.

[0124] As described above, the outlet of the second secondary oil passage 181 is slightly bent. As a result, the outlet of the second secondary oil passage 181 faces the annular gap 385 between the oil guide member 350 and the outer surface of the first shaft portion 44a of the outer shaft 44. Therefore, a portion of the lubricating oil diverted from the first secondary oil passage 180 to the second secondary oil passage 181 is supplied from the outlet of the second secondary oil passage 181 toward the oil receiving recess 340. The lubricating oil moves from the oil receiving recess 340 toward the annular gap 385 between the rotating shaft 40 and the oil guide member 350. The lubricating oil that enters the annular gap 385 passes through the first oil supply passage 386 and flows in the order of flow space 374, flow space 360, flow space 353, second oil supply passage 3582, and flow space 362. That is, the lubricating oil flows through the rotor internal oil passage 354.

[0125] The opening of the hole in the second magnet stopper 358 (the outlet of the rotor internal oil passage 354) is covered by the disc portion 392 of the second internal stopper 90. Therefore, the lubricating oil flowing out from the rotor internal oil passage 354 comes into contact with the disc portion 392. This contact prevents the lubricating oil from flowing toward the second bearing 84.

[0126] As shown in Figure 9, the second sub-housing 20 has a first drain hole 198, a second drain hole 197, and a second drain passage 196. Lubricating oil that flows out from the rotor oil passage 354 and comes into contact with the disc portion 392 flows into the second drain passage 196 via the first drain hole 198. On the other hand, lubricating oil that comes into contact with the second bearing 84 flows into the second drain passage 196 via the second drain hole 197. Thus, the second drain passage 196 is a second oil conduit that leads lubricating oil to the gas-liquid separator 302 (see Figure 12). The first drain hole 198, the second drain hole 197, and the second drain passage 196 are also part of the first oil recovery passage and discharge the lubricating oil that is recovered by the gas-liquid separator 302.

[0127] As shown in Figure 9, in the second sub-housing 20, three oil receiving holes 186 are opened on the end face facing the rotating electric machine system 10. The oil receiving holes 186 are located diametrically outward from the first downstream communication holes 1681-1683. The oil receiving holes 186 are input ports for lubricating oil.

[0128] Three third secondary oil passages 188 are provided inside the second sub-housing 20. The third secondary oil passages 188 extend radially along the diametrical direction of the second sub-housing 20. However, the third secondary oil passages 188 are formed in a phase different from that of the air relay passage 166. In addition, three oil outlet holes 190 are formed on the end face of the second sub-housing 20 facing the gas turbine engine 200. The hollow pin portion 193 of the oil distributor 192 is fitted into the oil outlet holes 190.

[0129] Inside the oil distributor 192, a first guide passage 1941 and a second guide passage 1942 are formed. The lubricating oil that has passed through the third auxiliary oil passage 188 is divided into lubricating oil that flows through the first guide passage 1941 and lubricating oil that flows through the second guide passage 1942. The outlet of the first guide passage 1941 is located at the second proximal end 862 of the second insertion hole 86. Therefore, the lubricating oil that flows out from the first guide passage 1941 comes into contact with the second bearing 84 from the second proximal end 862. The above is another part of the first oil supply passage.

[0130] The second guide channel 1942 branches off from the first guide channel 1941 midway. The exit of the second guide channel 1942 is connected to the second oil supply hole 195 formed in the second bearing holder 88. Therefore, the lubricating oil that has passed through the second guide channel 1942 flows out from the second oil supply hole 195 and comes into contact with the second bearing 84.

[0131] As shown in Figure 10, the space formed by the rectifier member 96 and the second outer stopper 92 communicates with the second drain passage 196 via the second drain hole 197. Therefore, lubricating oil that enters the space flows into the second drain passage 196 via the second drain hole 197.

[0132] The gas-liquid separator 302 shown in Figure 12 includes a first oil supply line 304, a first oil recovery line 305, an exhaust line 306, a second oil supply line 310, and a second oil recovery line 312. The first oil recovery line 305 includes a first relay pipe 3001, a second relay pipe 3002, and a third relay pipe 3003. The first drain passage 184 is connected to the gas-liquid separator 302 via the first relay pipe 3001. The second drain passage 196 is connected to the gas-liquid separator 302 via the second relay pipe 3002. The exhaust passage 172 is connected to the gas-liquid separator 302 via the third relay pipe 3003. The first oil supply line 304 is also connected to the input passage 174, which is the uppermost part of the first oil supply line.

[0133] As can be understood from this, the gas-liquid separator 302 recovers the compressed air and lubricating oil that have flowed inside the rotating electric machine housing 14 and resupplies them inside the rotating electric machine housing 14. In this way, the gas-liquid separator 302 constitutes an oil circulation supply system. A circulation pump 308, which constitutes an oil circulation supply system, is provided between the first oil supply line 304 and the first oil recovery line 305. The circulation pump 308 is also located between the second oil supply line 310 and the second oil recovery line 312.

[0134] As described later, the lubricating oil that flows out from the first drain passage 184 and the second drain passage 196 contains compressed air. In other words, the lubricating oil that flows from the first oil recovery line 305 into the gas-liquid separator 302 is a gas-liquid mixture. In the gas-liquid separator 302, the gas-liquid mixture is separated into lubricating oil and air. The lubricating oil is temporarily stored in the tank 318. After that, the lubricating oil is drawn out of the tank 318 by the circulation pump 308 and resupplied to the input passage 174 via the first oil supply line 304. Meanwhile, the air is released into the atmosphere via the exhaust line 306.

[0135] The rotating electric machine housing 14 has an input pipe section 314 as a second oil supply passage and an output pipe section 316 as a second oil recovery passage. The input pipe section 314 is provided near the second end of the main housing 16. The output pipe section 316 is provided on the side of the first casing 26. The input pipe section 314 and the output pipe section 316 are hollow sections having internal passages. The internal passage of the input pipe section 314 communicates with the stator chamber 23, and the internal passage of the output pipe section 316 communicates with the contact chamber 290 of the first casing 26 (see Figure 11).

[0136] The second oil supply line 310 branches off from the first oil recovery line 305, for example, and is connected to the input pipe section 314. Therefore, a portion of the lubricating oil stored in the tank 318 is supplied to the stator chamber 23 via the second oil supply line 310 and the input pipe section 314. In the stator chamber 23, the lubricating oil flows, for example, through the stator inner circumference oil passage 454. The lubricating oil can also pass through the slots of the stator 36 or the gaps between the electromagnetic coils 110, etc.

[0137] The direction of lubrication oil flow in the stator chamber 23 is the second direction, from the second end to the first end. This ensures that lubrication oil flows sufficiently to both the first and second ends of the electromagnetic coil 110. As described above, the stator chamber 23 is in communication with the contact chamber 290 of the first casing 26. Therefore, the lubrication oil flows into the contact chamber 290 of the first casing 26. Here, the output tube section 316 is connected to the second oil recovery line 312. Therefore, the lubrication oil in the contact chamber 290 is recovered to the gas-liquid separator 302 via the output tube section 316 and the second oil recovery line 312.

[0138] Next, the gas turbine engine 200 will be described. As shown in Figure 13, the gas turbine engine 200 comprises 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 electric machine system 10. The outer housing 2022 is connected to the inner housing 2021. The outer housing 2022 is the housing body.

[0139] As shown in Figures 1 and 9, the inner housing 2021 has a first annular portion 206, a second annular portion 208, and a plurality of legs 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 legs 210 connect the first annular portion 206 and the second annular portion 208. In the illustrated example, there are six legs 210. However, the number of legs 210 is determined according to the required coupling strength between the gas turbine engine 200 and the rotating electric machine system 10. That is, the number of legs 210 is not limited to the six shown in the illustrated example.

[0140] A cylindrical cover portion 212 protrudes from the central opening of the second annular portion 208 toward the rotating electric machine system 10. The right end of the leg portion 210 is connected to both sides of the cylindrical cover portion 212. An intake space 214 is formed between the leg portions 210.

[0141] As shown in Figures 9 and 13, each of the six leg portions 210 has an individual extraction passage 216 formed inside. The inlet of each extraction passage 216 is formed individually at the connection point with the cylindrical cover portion 212 in the leg portion 210. The outlet of each extraction passage 216 is formed individually at the end face of the first annular portion 206 facing the second sub-housing 20. All outlets of the extraction passages 216 are located on the circumference of a virtual circle. Therefore, all outlets of the extraction passages 216 overlap with the annularly shaped collection passage 162. In other words, all of the extraction passages 216 are in communication with the collection passage 162. In this way, compressed air from the multiple extraction passages 216 flows into and collects in the collection passage 162.

[0142] An air vent 217 is formed in the leg portion 210. The air vent 217 extends linearly from the inner wall to the outer wall of the cylindrical cover portion 212. The air vent 217 may 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 vents 217. Furthermore, forming an air vent 217 is not mandatory.

[0143] As shown in Figure 13, an annular engagement recess 218 is formed on the right end face of the second annular portion 208. The engagement recess 218 positions and fixes the shroud case 220 and the diffuser 226 (described later).

[0144] As shown in Figure 13, the gas turbine engine 200 further comprises a shroud case 220, a compressor wheel 222, a turbine wheel 224, a diffuser 226, a combustor 228, and a nozzle 230.

[0145] The shroud case 220 is hollow and larger than the rectifier member 96. The small-diameter left end of the shroud case 220 faces the rectifier 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 shroud case 220 gradually decreases in diameter from the right end to the left end, but the tip of the left end curves to expand outward in the diametrical direction.

[0146] The left end of the shroud case 220 is exposed to the intake space 214. The top portion 102 of the rectifier member 96 enters the interior of the left end of the shroud case 220. An annular closing flange portion 232 is provided on the curved side circumferential 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.

[0147] In the side wall of the shroud case 220, an air vent 234 is formed between the closing flange portion 232 and the first engaging projection 238. The air vent 234 extends from the inner surface to the outer surface of the side wall of the shroud case 220. The air vent 234 is the inlet to the chamber 236 when compressed air enters the chamber 236.

[0148] Chamber 236 is interposed between the extraction port 234 and the extraction passage 216. In other words, chamber 236 connects the extraction port 234 and the extraction passage 216. Chamber 236 is also open to the atmosphere through an air vent 217.

[0149] A first engaging projection 238 protrudes from the right end of the shroud case 220 toward the second annular portion 208. The first engaging projection 238 engages with an engaging recess 218 of the second annular portion 208. This engagement, along with the contact of the outer edge of the closing flange portion 232 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. Simultaneously, a chamber 236 is formed, surrounded by the leg portion 210, the cylindrical cover portion 212 and the second annular portion 208, and the closing flange portion 232, side circumferential wall and first engaging projection 238 of the shroud case 220. The chamber 236 forms an annular shape surrounding the shroud case 220.

[0150] The compressor wheel 222 and the turbine wheel 224 can rotate integrally with the rotating shaft 40 and the output shaft 204. Specifically, as shown in detail in Figure 5, the compressor wheel 222 has a small-diameter cylindrical portion 242 at its left end. This small-diameter cylindrical portion 242 enters into a through 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. This first external spline 239 engages with a first internal spline 66 formed on the right open end 442 of the outer shaft 44.

[0151] The right open end 442 of the outer shaft 44 is press-fitted into the hollow interior of the small-diameter cylindrical portion 242. As a result, the inner circumferential wall of the left opening of the small-diameter cylindrical portion 242 presses against the outer circumferential wall of the right open end 442 of the outer shaft 44 inward in the diametrical direction. The compressor wheel 222 is connected to the outer shaft 44 (rotating shaft 40) by the above-described meshing and press-fitting.

[0152] A through-hole 240 is formed at the center of the diameter of the compressor wheel 222, extending in the left-right direction. In this through-hole 240, a second external spline 246 is engraved on the inner wall at the left end. Furthermore, in the through-hole 240, the diameter of the hole where it connects to the hollow interior of the small-diameter cylindrical portion 242 is slightly smaller than that of other parts. 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 small-diameter cylindrical portion 242 side. In the area where the inner flange portion 248 is provided, the diameter of the through-hole 240 is at its minimum.

[0153] 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 that protrudes from the through hole 240 enters the connecting hole 62 of the rotating shaft 40. A male threaded portion 252 is engraved on the left end of the output shaft 204. The male threaded portion 252 is screwed into a female threaded portion 64 formed on the inner wall of the connecting hole 62. This screwing connects the rotating shaft 40 and the output shaft 204.

[0154] A second internal spline 254 is formed near the left end of the output shaft 204. The second internal spline 254 engages with a second external spline 246 formed on the inner circumferential wall of the through hole 240. The left end of the output shaft 204 is press-fitted into the inner flange portion 248.

[0155] As shown in Figure 13, 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.

[0156] As shown in Figure 14, the ring member 256 has a fitting hole 258 extending from the compressor wheel 222 to the turbine wheel 224. In addition, multiple (for example, three) labyrinth-forming protrusions 264 are formed on the outer peripheral wall of the ring member 256. The labyrinth-forming protrusions 264 project outward in the diametrical 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 burnt fuel (exhaust gas) generated in the combustor 228 from flowing back into the compressor wheel 222.

[0157] In the compressor wheel 222, an annular projection 268 protrudes from the right end face facing the turbine wheel 224. When the left end face of the ring member 256 seats on the right end face of the compressor wheel 222, the annular projection 268 is fitted into the fitting hole 258. On the other hand, in the turbine wheel 224, the output shaft 204 extends from the left end face facing the compressor wheel 222. Also, a fitting projection 270 surrounding the output shaft 204 is formed on the left end face. When the right end face of the ring member 256 seats on the left end face of the turbine wheel 224, the top surface of the fitting projection 270 is fitted into the fitting hole 258. As a result, parts of the compressor wheel 222 and the turbine wheel 224 are 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.

[0158] The labyrinth-forming protrusion 264 is surrounded by the intermediate plate 266 inside the hollow interior of the outer housing 2022 (see Figure 13). 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 in contact with 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. Since the pressure of the compressed air is higher than the pressure of the combustion gas, it is possible to suppress the combustion gas from passing through the labyrinth-forming protrusion 264 and flowing into the space surrounding the compressor wheel 222.

[0159] As shown in Figure 13, within the hollow interior of the outer housing 2022, parts of the shroud case 220 and compressor wheel 222, along with the intermediate plate 266, are surrounded by the diffuser 226. A second engaging projection 273 is formed at the left end of the diffuser 226. The second engaging projection 273 engages with the engaging recess 218 together with the first engaging projection 238 of the shroud case 220. This engagement positions and fixes the diffuser 226 to the inner housing 2021.

[0160] Inside the hollow outer housing 2022, the turbine wheel 224 is surrounded by the nozzle 230, and the nozzle 230 is surrounded by the 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 on the right end face of the outer housing 2022. The fuel supply nozzle 275 supplies fuel to the combustor 228.

[0161] The combustor 228 has a relay hole 276 that connects the combustion air passage 274 to the inside of the combustor 228. As will be described later, the combustion air compressed by the compressor wheel 222 reaches the inside of the combustor 228 via the diffuser 226, the combustion air passage 274, and the relay hole 276. The combustor 228 also has micropores (not shown). The air discharged from the micropores forms an air curtain that cools the inside of the combustor 228.

[0162] The nozzle 230 has a portion that surrounds the largest diameter part of the turbine wheel 224. This portion has a discharge hole (not shown) for supplying fuel, which has been burned together with the combustion air, to the turbine wheel 224. In the following, the burned fuel will also be referred to as "burned fuel." "Burned fuel" is synonymous with "combustion gas" or "exhaust gas after combustion."

[0163] An outlet 280 is open at the right end of the outer housing 2022 and nozzle 230. The burnt fuel passes through the discharge hole and proceeds into the nozzle 230, and is then blown out of the outer housing 2022 through the outlet 280 by the rotating turbine wheel 224. Although not specifically shown in the figures, an outlet 280 is provided with an outlet pipe for discharging the burnt fuel.

[0164] The rotating electric machine system 10 and the combined power system 500 according to this embodiment are basically configured as described above. Next, the operation and effects of the rotating electric machine system 10 and the combined power system 500 will be explained.

[0165] When assembling the rotating electric machine system 10, a partition member 410 is inserted between the rotor 34 and the stator 36. For example, the second end of the partition member 410 is inserted into the clearance between the rotor 34 and the stator 36 at the first end. The partition member 410 is pushed in such a way that the second end faces the second sub-housing 20. At this time, the inner circumferential wall of the second end slides against the outer circumferential wall of the tapered portion 467. This guides the second end of the partition member 410 into the annular guide 466. As the second end of the partition member 410 is pushed further toward the second sub-housing 20, it is sandwiched between the annular guide 466 and the annular holder 460. In this way, by providing the annular guide 466 inside the rotating electric machine housing 14, it becomes easy to guide the partition member 410 into the annular holder 460.

[0166] First, a direct current is supplied from the battery 146. The conversion circuit 152 of the current converter 150, shown in Figures 2 and 8, converts this direct current into an alternating current. The alternating current is supplied to the electromagnetic coils 110 (U-phase coil, V-phase coil, and W-phase coil) via the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443. As the alternating current flows through the electromagnetic coils 110, an alternating magnetic field is generated in the stator 36. As a result, attractive and repulsive forces alternately act between the electromagnetic coils 110 and the permanent magnets 72 of the rotor 34. Consequently, the rotating shaft 40 begins to rotate. Alternatively, the rotating shaft 40 may be rotated by a known starter (not shown).

[0167] As shown in Figure 5, 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. In addition, 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. As a result, the rotational torque of the rotating shaft 40 is quickly transmitted to the output shaft 204 via the compressor wheel 222.

[0168] In other words, when the rotating shaft 40 starts to rotate, the output shaft 204 also starts to rotate integrally with the rotating shaft 40. Consequently, the compressor wheel 222 and turbine wheel 224, which are supported by the output shaft 204, rotate integrally with the output shaft 204. As described above, by engaging the first internal spline 66 with the first external spline 239 and engaging 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.

[0169] Furthermore, 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. Also, the left end of the output shaft 204 is press-fitted into the inner flange portion 248 of the compressor wheel 222. As a result, the axis of the rotating shaft 40 and the axis of the output shaft 204 are precisely aligned. This effectively suppresses eccentric or vibrating rotation of the output shaft 204.

[0170] In addition, as shown in Figure 14, a ring member 256 is interposed between the compressor wheel 222 and the turbine wheel 224. The fitting hole 258 of the ring member 256 is fitted with the annular projection 268 on the right end face of the compressor wheel 222 and the fitting projection 270 on the left end face of the turbine wheel 224. These fittings also contribute to suppressing the eccentric rotation (vibration) of the output shaft 204. Therefore, there is no need to provide a mechanism to suppress vibration. Furthermore, there is no need to increase the diameter of the output shaft 204. As a result, the combined power system 500 can be miniaturized.

[0171] Furthermore, frictional force is generated between the right end face of the compressor wheel 222 and the left end face of the ring member 256. Frictional force is also generated between the right end face of the ring member 256 and the left end face of the turbine wheel 224. This frictional force causes the compressor wheel 222, the ring member 256, and the turbine wheel 224 to be in close contact with each other. Consequently, rotational misalignment between the two wheels 222 and 224 is prevented.

[0172] Furthermore, when assembling the combined power system 500, the above fitting ensures that the compressor wheel 222 and turbine wheel 224 are aligned (centered) with respect to the output shaft 204. It is preferable to provide a ring member 256 between the two wheels 222 and 224, and to individually fit a portion of both wheels 222 and 224 into the fitting holes 258 of the ring member 256. This facilitates the centering of the compressor wheel 222 and turbine wheel 224 with respect to the output shaft 204.

[0173] As a result of the above rotation, as shown in Figure 13, air is drawn into the shroud case 220 through the intake space 214 between the legs 210 of the inner housing 2021. Here, a flow straightening member 96 is located at the center of the diameter of the inner housing 2021. As described above, the flow straightening member 96 has a mountain-like shape that narrows in diameter as it approaches the shroud case 220. Moreover, the surface of the narrowed diameter portion 100 is smooth. Therefore, the air being drawn in is straightened by the flow straightening member 96 so that it is directed towards the shroud case 220. Since the right end of the flow straightening member 96 enters from the left end opening of the shroud case 220, the air is efficiently guided into the shroud case 220. In this way, by shaping the flow straightening member 96 as described above and having its top portion 102 enter into the shroud case 220, air can be efficiently collected in the shroud case 220.

[0174] The air drawn into the shroud case 220 flows between the compressor wheel 222 and the shroud case 220. Since 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 during this flow. In other words, compressed air is generated.

[0175] An air vent 234 is formed in the shroud case 220. As a result, a portion of the compressed air flows from the air vent 234 into the chamber 236. In other words, the compressed air is diverted. The chamber 236 is annular and has a larger volume than the air vent 234. Therefore, the compressed air that flows into the chamber 236 is temporarily stored in the chamber 236.

[0176] Since multiple extraction passages 216 are formed, compressed air is distributed from the chamber 236 to each extraction passage 216. In this case, there may be pressure differences among the distributed curtain air. However, in this embodiment, the compressed air (curtain air) that has passed through the extraction port 234 flows into a single annular chamber 236. As a result, the pressure of the curtain air in the chamber 236 becomes uniform. In other words, the pressure of the curtain air is made uniform. Thus, the chamber 236 is a pressure adjustment chamber that adjusts the pressure of the curtain air to be approximately constant.

[0177] As described above, the curtain air flowing in from the extraction port 234 is part of the compressed air and is therefore at high pressure. Here, since the volume of the chamber 236 is larger than the volume of the extraction port 234, the curtain air diffuses as it flows into the chamber 236. As a result, the pressure of the curtain air decreases. As can be understood from this, the chamber 236 also serves as a buffer chamber that reduces the pressure of the compressed air.

[0178] The inner housing 2021 has an air vent 217 in addition to the extraction passage 216. Excess compressed air is released to the outside (atmosphere) of the gas turbine engine 200 through the air vent 217. This prevents the curtain air pressure in the chamber 236 from rising excessively. In other words, the air vent 217 allows for easy adjustment of the pressure inside the chamber 236.

[0179] Within the chamber 236, the inlets of the extraction passages 216, each individually formed in the six legs 210, are open. Therefore, the curtain air within the chamber 236 then flows individually through the six extraction passages 216, thereby proceeding towards the second sub-housing 20. As described above, the pressure of the curtain air is approximately constant at this point.

[0180] As shown in Figure 9, the outlets of all six extraction passages 216 overlap with the collection passage 162. Therefore, the curtain air that has flowed through the six extraction passages 216 flows into the collection passage 162, collects there, and diffuses in an annular pattern along the collection passage 162. In this process, the pressure of the curtain air is further homogenized.

[0181] The curtain air then flows individually from the collective channel 162 into three upstream communication holes 164 and circulates individually along three air relay paths 166. Subsequently, a portion of the curtain air is discharged from the first downstream communication holes 1681-1683. The remaining portion of the curtain air is discharged from the second downstream communication holes 1701-1703. Hereafter, the curtain air (compressed air) discharged from the first downstream communication holes 1681-1683 will be referred to as "first branch air," and the curtain air (compressed air) discharged from the second downstream communication holes 1701-1703 will be referred to as "second branch air."

[0182] The path of the first branched air will now be described. The first downstream communication hole 1681 communicates with the hollow interior of the first hollow pipe section 1601. The first downstream communication hole 1682 communicates with the hollow interior of the second hollow pipe section 1602. The first downstream communication hole 1683 communicates with the hollow interior of the third hollow pipe section 1603. Therefore, the first branched air flows through the hollow interiors of the first hollow pipe sections 1601 to the third hollow pipe sections 1603 as shown in Figure 1, etc., and proceeds from the second end to the first end of the rotating electric machine housing 14. That is, before the first branched air enters the rotor chamber 22 inside the rotating electric machine housing 14, the direction of flow of the first branched air is the second direction.

[0183] The first hollow tube section 1601 to the third hollow tube section 1603 are located on the outer circumference of the cooling jacket 24. A cooling medium is pre-circulated in the cooling jacket 24. Therefore, as the first branch air flows along the first hollow tube section 1601 to the third hollow tube section 1603, the heat from the first branch air is sufficiently conducted to the cooling medium. As a result, the first branch air becomes relatively cold. In other words, in this embodiment, the first branch air can be cooled by the cooling jacket 24, which is used to cool the rotating electric machine 12 and the current converter 150, etc.

[0184] For the reasons stated above, 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. Therefore, the combined power system 500 can be made smaller.

[0185] The first branched air, having flowed through the first hollow tube section 1601 to the third hollow tube section 1603, flows into the three starting channels 450 via the flexible tubes 470a to 470c. The first branched air then flows through the starting channels 450 into the rotor chamber 22, which is formed diametrically inward of the partition wall member 410.

[0186] A portion of the first diverted air then flows toward the first insertion hole 78 via the first air branching path L in the rotor chamber 22. The remaining portion of the first diverted air flows toward the second insertion hole 86 via the second air branching path M in the rotor chamber 22, along the clearance between the outer wall of the permanent magnet 72 and the inner circumferential wall of the partition member 410. In this way, the first diverted air is divided into compressed air that flows toward the first insertion hole 78 at the left end (first end) and compressed air that flows toward the second insertion hole 86 at the right end (second end).

[0187] A portion of the first branch air flows through the clearance between the outer wall of the permanent magnet 72 and the inner circumferential wall of the partition member 410, thereby cooling the rotor 34. In the rotor chamber 22, the direction of flow of the first branch air is the first direction, from the first end to the second end. Here, as described above, the first branch air is sufficiently cooled by the cooling jacket 24. Therefore, the rotor 34 is efficiently cooled.

[0188] Furthermore, in this embodiment, the rotating electric machine 12 is cooled using compressed air generated by the gas turbine engine 200. Therefore, there is no need to supply cooling air to the rotor chamber 22 to cool the rotor 34. This makes it possible to simplify the configuration of the combined power system 500 while cooling the rotor 34.

[0189] As shown in Figure 7, the inner separation distance Din between the permanent magnet 72 and the inner circumferential wall of the partition member 410 is greater than the outer separation distance Dout between the outer circumferential wall of the partition member 410 and the electromagnetic coil 110. Preferably, Din is about 3.5 to 4 times Dout. This suppresses the generation of turbulence in the compressed air flowing between the permanent magnet 72 and the partition member 410. It also suppresses the generation of large frictional heat in the permanent magnet 72.

[0190] A portion of the first branched air that flows toward the first insertion hole 78 reaches the first proximal end 782 of the first insertion hole 78. At this first proximal end 782, a portion of the first branched air forms an air curtain for the first bearing 74. Meanwhile, the remaining portion of the first branched air that flows toward the second insertion hole 86 reaches the second distal end 861 of the second insertion hole 86 via the third sub-branch 941. At this second distal end 861, the remaining portion of the first branched air forms an air curtain for the second bearing 84.

[0191] The excess first branch air is recovered by the gas-liquid separator 302 (oil circulation supply device) via the exhaust passage 172 and the third relay pipe 3003.

[0192] The path of the second branch air will now be described. The second downstream communication holes 1701 to 1703 each individually overlap with three inlets 104 formed in the base portion 98 of the flow straightening member 96. Therefore, the second branch air flows into the relay chamber 106 (the hollow interior of the flow straightening member 96) via the inlets 104.

[0193] 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 branched air flowing into the relay chamber 106 comes into contact with the small-diameter cylindrical portion 242. A portion of the second branched air then flows toward the fourth sub-branch 942. The remainder of the second branched air flows toward the outlet 943.

[0194] A portion of the second branch air reaches the second proximal end 862 of the second insertion hole 86 via the fourth sub-branch 942. At this second proximal end 862, a portion of the second branch air forms an air curtain for the second bearing 84. In this way, the second bearing 84 is sandwiched between the remaining portion of the second branch air that reached the second proximal end 862 and a portion of the first branch air that reached the second distal end 861.

[0195] The remaining portion of the second branch air is discharged into the left end of the shroud case 220 via the outlet passage 943. As described above, intake air is drawn in at the left end opening of the shroud case 220. Therefore, the remaining portion of the second branch air is compressed by the compressor wheel 222 together with the drawn-in atmosphere.

[0196] 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, pressure distribution in the curtain air is avoided. Furthermore, surging in the curtain air is also avoided. As a result, it is possible to supply the curtain air around the first bearing 74 and the second bearing 84 while maintaining the curtain air pressure at a substantially constant level.

[0197] As described above, the relay chamber 106 widens as it approaches the fourth sub-branch 942. Moreover, the second branch air flowing out of the relay chamber 106 is divided into a portion that goes towards the fourth sub-branch 942 and the remainder that goes towards the exit channel 943. Consequently, the pressure of the second branch air reaching the second proximal end 862 is lower than the pressure of the second branch air before it flowed into the relay chamber 106. As a result, the pressure of the first branch air reaching the second distal end 861 and the pressure of the second branch air reaching the second proximal end 862 are in equilibrium.

[0198] Next, the lubrication oil pathway will be described. A portion of the lubrication oil is supplied to the first bearing 74 and the second bearing 84 as a lubricant. The remainder of the lubrication oil is supplied to the rotating shaft 40 and the stator 36 as a cooling oil to cool the rotating electric machine 12.

[0199] Lubricating oil is drawn from the tank 318 shown in Figure 12 to the first oil supply line 304 by a circulation pump 308. Most of the lubricating oil flows through the first oil supply line 304 and is then supplied to an input passage 174 formed in the main housing 16. The lubricating oil flows from the input passage 174 into the main oil passage 176. The main oil passage 176 branches into a first oil branch passage N leading to the first sub-housing 18 and a second oil branch passage R leading to the second sub-housing 20. Therefore, the lubricating oil is divided into lubricating oil flowing along the first oil branch passage N and lubricating oil flowing along the second oil branch passage R.

[0200] A portion of the lubricating oil that flows along the first oil branch channel N flows into the first auxiliary oil channel 180 through the first inlet hole 178 formed in the first sub-housing 18. A portion of the lubricating oil flowing through the first auxiliary oil channel 180 further flows from the first auxiliary oil channel 180 into the second auxiliary oil channel 181. Hereinafter, the lubricating oil that flows along the first auxiliary oil channel 180 and is discharged from the outlet of the first auxiliary oil channel 180 will be referred to as the "first branch oil". The lubricating oil that flows along the second auxiliary oil channel 181 and is discharged from the outlet of the second auxiliary oil channel 181 will be referred to as the "first cooling oil". The lubricating oil that flows along the second oil branch channel R will be referred to as the "second branch oil".

[0201] The first branched oil discharged from the outlet of the first auxiliary oil passage 180 is supplied to the first distal end 781 of the first insertion hole 78 through the first oil supply hole 182 formed in the first bearing holder 80. At this time, the first branched oil is guided by the upstream guide groove 390 of the oil guide member 350 and the downstream guide groove 368 formed in the first outer stopper 81 toward the first bearing 74. The first branched oil further enters the inner bore of the first bearing 74 and lubricates the first bearing 74.

[0202] The first branching oil that flows from the first distal end 781 to the first proximal end 782 is blocked by the first branching air (air curtain) that reaches the first proximal end 782. Therefore, the first branching oil is prevented from flowing toward the first air branching path L. As a result, the first branching oil is also prevented from entering the rotor chamber 22. This makes it possible to prevent the permanent magnet 72 from being contaminated with the first branching oil.

[0203] The excess first flow oil flows into the hollow recess 118. The first drain passage 184 is connected to the hollow recess 118. Therefore, the first flow oil in the hollow recess 118 is recovered by the gas-liquid separator 302 via the first drain passage 184.

[0204] The second branched oil, having flowed through the second oil branch channel R, flows into the third auxiliary oil channel 188 through the oil receiving hole 186 formed in the second sub-housing 20. The second branched oil, having flowed through the third auxiliary oil channel 188, is divided into the first guide channel 1941 and the second guide channel 1942 formed inside the oil distributor 192. A portion of the second branched oil that flows out from the outlet of the first guide channel 1941 is supplied to the second proximal end 862 of the second insertion hole 86. The remainder of the second branched oil that has passed through the second guide channel 1942 is supplied to the second bearing 84 through the second oil supply hole 195 formed in the second bearing holder 88. The second branched oil enters the inner bore of the second bearing 84 and lubricates the second bearing 84.

[0205] The second branching oil that enters the inner bore of the second bearing 84 is surrounded by the first branching air supplied to the second distal end 861 and the second branching air supplied to the second proximal end 862. As described above, the pressure of the first branching air supplied to the second distal end 861 and the pressure of the second branching air supplied to the second proximal end 862 are in equilibrium. Therefore, the flow of the second branching oil toward the third sub-branch 941 or the fourth sub-branch 942 is prevented. As a result, the second branching oil is prevented from entering between the rotating shaft 40 and the electromagnetic coil 110. Furthermore, the second branching oil is prevented from entering the relay chamber 106 of the flow straightening member 96. This prevents the permanent magnet 72 and the flow straightening member 96 from being contaminated with the second branching oil.

[0206] As described above, the pressure of the curtain air is adjusted to be approximately constant. Therefore, an air curtain of a predetermined pressure is continuously formed around the first bearing 74 and the second bearing 84. This prevents lubricating oil from leaking from the first bearing 74 and the second bearing 84.

[0207] The excess second branch oil flows into the space formed by the flow straightening member 96 and the second outer stopper 92. The second sub-housing 20 has a second drain hole 197 and a second drain passage 196. The second branch oil that flows into the space is collected by the gas-liquid separator 302 via the second drain hole 197 and the second drain passage 196.

[0208] As described above, the first branch oil lubricates the first bearing 74, and the second branch oil lubricates the second bearing 84. This prevents seizure from occurring in the first bearing 74 and the second bearing 84.

[0209] The path of the first cooling oil flowing through the second auxiliary oil passage 181 will now be described. As described above, the outlet of the second auxiliary oil passage 181 faces the annular gap 385 between the oil guide member 350 and the outer surface of the first shaft portion 44a of the outer shaft 44 (see Figure 7). Therefore, as shown in Figure 7, the first cooling oil is discharged from the outlet of the second auxiliary oil passage 181 toward the annular gap 385.

[0210] At this point, the rotating shaft 40 has started to rotate. Therefore, the lubricating oil that has entered the oil receiving recess 340 moves to the annular groove 384 located on the outer circumference of the oil receiving recess 340 due to the action of centrifugal force. Since the oil receiving recess 340 and the annular groove 384 have sufficient volume, it is possible to temporarily store a predetermined amount of first cooling oil in the oil receiving recess 340 and the annular groove 384.

[0211] The annular groove 384 communicates with the rotor internal oil passage 354 via a first oil supply passage 386 formed in the oil guide member 350. Therefore, the first cooling oil flows into the rotor internal oil passage 354 via the first oil supply passage 386. The first cooling oil then flows through the rotor internal oil passage 354 toward the first drain hole 198.

[0212] During this flow process, the first cooling oil passes through the first stage 330, the second stage 332, the third stage 334, and the fourth stage 336 (see Figure 6). As a result, the first cooling oil moves smoothly outward in the diametrical direction of the rotating shaft 40 as it moves from upstream to downstream in the flow direction of the first cooling oil. Thus, as the first cooling oil passes through the first stage 330, the second stage 332, the third stage 334, and the fourth stage 336, it flows along a direction other than the axial direction of the rotating shaft 40.

[0213] As the rotating shaft 40 rotates, centrifugal force acts on the first cooling oil flowing through the rotor's internal oil passage 354. This centrifugal force causes the first cooling oil to tend to move outward in the diametrical direction of the rotating shaft 40. As described above, the outer shaft 44 constituting the rotating shaft 40 is provided with a first stage 330, a second stage 332, a third stage 334, and a fourth stage 336. These direction-changing sections cause the first cooling oil to move outward in the diametrical direction of the rotating shaft 40.

[0214] The first coolant flowing through the rotor's internal oil passage 354 is subjected to a force acting outward in the diametrical direction of the rotating shaft 40 and a force acting axially on the rotating shaft 40. Therefore, the first coolant tends to flow in the direction of the combined force of these two forces. This prevents the first coolant from being concentrated on, for example, the inner circumferential wall of the inner bore 73 of the cylindrical member 70. Consequently, obstruction of the flow of the first coolant due to such uneven distribution is avoided. In other words, despite centrifugal force acting on the first coolant, it can be allowed to flow smoothly along the axial direction of the rotating shaft 40.

[0215] As the first cooling oil flows through the internal oil passage 354 of the rotor, it comes into contact with the outer surface of the outer shaft 44. As a result, the outer shaft 44 is cooled. At the same time, the first cooling oil comes into contact with the inner circumferential wall of the inner bore 73 of the cylindrical member 70. Consequently, the cylindrical member 70 and the permanent magnet 72 are cooled. In this way, an excessive rise in the temperature of the rotor 34 is suppressed.

[0216] In other words, the temperature of the permanent magnet 72 is prevented from rising due to cooling by the first branch air and the first cooling oil. Therefore, the temperature of the permanent magnet 72 is prevented from reaching the Curie temperature. As a result, the reduction in the magnetic force of the permanent magnet 72 can be prevented.

[0217] The first cooling oil that flows out from the outlet (flow space 362) of the rotor oil passage 354 comes into contact with the disc portion 392. As shown in Figure 10, the first cooling oil flows into the second drain passage 196 through the first drain hole 198 formed in the second sub-housing 20. In the second drain passage 196, the first cooling oil merges with the second branched oil and is then recovered by the gas-liquid separator 302.

[0218] As can be understood from this, the disc portion 392 prevents the first coolant from moving toward the second bearing 84. Therefore, even if dust or other particles are mixed into the first coolant, it is prevented from reaching the second bearing 84. In addition, it is prevented the first coolant, whose temperature has risen as it flows through the rotor oil passage 354, from coming into contact with the second bearing 84. Therefore, it is prevented the temperature of the second bearing 84 from rising excessively.

[0219] A portion of the lubricating oil drawn from tank 318 flows into the second oil supply line 310, which branches off from the first oil supply line 304. Hereafter, the lubricating oil circulating in the second oil supply line 310 will be referred to as the "second cooling oil."

[0220] The second coolant flows through the second oil supply line 310 and then reaches the input pipe section 314. Since the input pipe section 314 is formed near the second end on the outer peripheral wall of the main housing 16, the second coolant flows into the second end side of the stator chamber 23. The second coolant flows from the second end to the first end of the stator chamber 23 due to the discharge force of the circulation pump 308. That is, the direction of flow of the second coolant in the stator chamber 23 is the second direction, from the second end to the first end.

[0221] In the stator chamber 23, which is an oil passage within the housing, the second cooling oil flows, for example, through the stator inner circumference oil passage 454. Alternatively, the second cooling oil flows through the gaps between the electromagnetic coils 110 in the stator 36. Or, the second cooling oil flows through the internal holes of the stator 36 (the gaps between the insulating substrates 112). In this way, the stator 36 is efficiently cooled by the contact of the second cooling oil with the stator 36.

[0222] As described above, in this embodiment, the rotor 34 is cooled by the first cooling oil and the first flow-divided air. Furthermore, the stator 36 is cooled by the second cooling oil. Therefore, the rotating electric machine 12 is sufficiently cooled. As a result, a predetermined magnetic force is generated in the alternating magnetic field formed between the permanent magnet 72 and the electromagnetic coil 110. This allows the rotating electric machine 12 to maintain a predetermined output. In addition, it is possible to increase the output by rotating the rotor 34 at high speed.

[0223] In the rotating electric machine housing 14, the flow direction of the first branch air circulating through the innermost rotor chamber 22 is the first direction. In the rotating electric machine housing 14, the flow direction of the cooling medium circulating through the outermost cooling jacket 24 is also the first direction. In contrast, the flow direction of the second cooling oil circulating through the stator chamber 23 located between the rotor chamber 22 and the cooling jacket 24 is the second direction. Thus, the flow direction of the fluid circulating diametrically inward of the rotating electric machine housing 14 and the flow direction of the fluid circulating diametrically outward of the rotating electric machine housing 14 are opposite to each other.

[0224] Therefore, for example, the first branch air, which has become hot after flowing through the rotor chamber 22, and the second cooling oil, which has become hot after flowing through the stator chamber 23, are prevented from overlapping in the diametrical direction of the rotating electric machine housing 14. In other words, the hot first branch air and the hot second cooling oil will not concentrate at the first or second end of the rotating electric machine housing 14. This prevents insufficient cooling of the rotor 34 and stator 36 at the first or second end of the rotating electric machine housing 14.

[0225] Furthermore, the second cooling oil, which becomes hot after flowing through the stator chamber 23, and the cooling medium, which becomes hot after flowing through the cooling jacket 24, are prevented from overlapping in the diametrical direction of the rotating electric machine housing 14. In other words, the hot second cooling oil and the hot cooling medium will not be concentrated at the first or second end of the rotating electric machine housing 14. This prevents insufficient cooling of the compressed air flowing through the first hollow tube section 1601 to the third hollow tube section 1603 at the first or second end of the rotating electric machine housing 14. In addition, insufficient cooling of the rotating electric machine 12 by the cooling medium flowing through the cooling jacket 24 is also prevented at the first or second end of the rotating electric machine housing 14.

[0226] The second coolant, having flowed through the stator chamber 23 (oil passage within the housing), flows from the first end of the stator chamber 23 into the contact chamber 290 of the first casing 26. As can be understood from this, the contact chamber 290 is located downstream of the stator chamber 23 in the direction of flow of the second coolant. The contact chamber 290 and the terminal chamber 291 are separated by the blocking protrusion 294 as described above. Therefore, the second coolant does not flow from the contact chamber 290 into the terminal chamber 291.

[0227] The second cooling oil in the contact chamber 290 comes into contact with the terminal portion 295, the terminal wire 110a, and the screw 296. This cools the electrical contact between the U-phase terminal 1441 and the U-phase coil. For the same reason, the electrical contact between the V-phase terminal 1442 and the V-phase coil is also cooled. The electrical contact between the W-phase terminal 1443 and the W-phase coil is also cooled.

[0228] The second cooling oil in the contact chamber 290 flows into the second oil recovery line 312 via the output pipe section 316. The lubricating oil that has flowed through the second oil recovery line 312 is recovered in the gas-liquid separator 302 shown in Figure 12.

[0229] As described above, the gas-liquid separator 302 recovers the first and second branch air (curtain air), the first branch oil, the second branch oil, the first cooling oil, and the second cooling oil (lubricating oil). Here, within the rotating electric machine housing 14, the first and second branch oils are blocked by an air curtain. For this reason, the curtain air exhausted from the exhaust passage 172 contains lubricating oil. In other words, the curtain air exhausted from the exhaust passage 172 is substantially a gas-liquid mixture.

[0230] In this embodiment, the oil circulation supply device includes a gas-liquid separator 302. Thus, the gas-liquid mixture is separated into air and lubricating oil. The air is released into the atmosphere via an exhaust line 306 provided in the gas-liquid separator 302. Meanwhile, the lubricating oil is temporarily stored in a tank 318. The lubricating oil in the tank 318 is drawn out of the gas-liquid separator 302 by a circulation pump 308. The lubricating oil is then resupplied from the gas-liquid separator 302 to the first bearing 74, the second bearing 84, and the rotor internal oil passage 354 via a first oil supply line 304, as described above. While the rotating shaft 40 rotates, the first bearing 74, the second bearing 84, and the rotor 34 are cooled by the lubricating oil.

[0231] In this way, by separating the gas-liquid mixture into lubricating oil and air in the gas-liquid separator 302, so-called air entrapment is avoided in the first oil supply line 304 and the circulation pump 308. Therefore, lubricating oil can be resupplied to the first bearing 74 and the second bearing 84 at an appropriate discharge pressure or flow rate. As a result, the first bearing 74 and the second bearing 84 are sufficiently lubricated. Consequently, seizure of the first bearing 74 and the second bearing 84 can be suppressed.

[0232] As described above, the curtain air (first and second branch air) prevents lubricating oil from scattering from the first bearing 74 and the second bearing 84. The curtain air is then discharged to the outside of the rotating electric machine housing 14 as described above. Therefore, even if lubricating oil leaks from the first bearing 74 or the second bearing 84, the leaked lubricating oil is carried by the curtain air and discharged to the outside of the rotating electric machine housing 14. Thus, it is possible to prevent the leaked lubricating oil from flowing toward the rotor 34. Furthermore, it is possible to prevent the leaked lubricating oil from remaining inside the rotor 34.

[0233] As described above, the pressure of the curtain air continuously supplied to the rotating electric machine housing 14 is approximately constant. Therefore, it is possible to continuously prevent the scattering of lubricating oil. Furthermore, even if lubricating oil leaks, the leaked lubricating oil can be continuously discharged to the outside of the rotating electric machine housing 14.

[0234] The compressed air that passes between the shroud case 220 and the compressor wheel 222 without entering the extraction port 234 becomes combustion air. As shown in Figure 13, the combustion air flows into the diffuser 226. The combustion air flows out from the outlet hole formed in the wall of the diffuser 226 into the combustion air passage 274 between the combustor 228 and the outer housing 2022. The combustion air then flows into the combustion chamber (the hollow interior of the combustor 228) through the intermediate hole 276 formed in the combustor 228, the aforementioned micropores, and the clearance between the combustor 228 and the fuel supply nozzle 275.

[0235] The combustor 228 is preheated. Consequently, 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, becoming high-temperature burnt fuel. When this burnt fuel is supplied into the nozzle 230 from the discharge hole, it expands within the nozzle 230. This causes the turbine wheel 224 to start rotating at high speed.

[0236] The output shaft 204 holds the 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 together at high speed. Simultaneously, the rotating shaft 40 also rotates at high speed. The burnt fuel is discharged outside the outer housing 2022 through a discharge pipe (not shown) provided at the discharge port 280.

[0237] The ring member 256 interposed between the compressor wheel 222 and the turbine wheel 224 also serves as a sealing member that seals the space between the two wheels 222 and 224. Furthermore, as shown in Figure 14, multiple labyrinth-forming protrusions 264 are formed on the outer peripheral wall of the ring member 256. These labyrinth-forming protrusions 264 abut against the inner wall of the hole 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. Combustion gas from the turbine wheel 224 also reaches the labyrinth-forming protrusions 264. As described above, the pressure of the compressed air is higher than the pressure of the combustion gas. Therefore, the flow of combustion gas through the labyrinth-forming protrusions 264 into the compressor wheel 222 is suppressed. For the reasons stated above, it is prevented, for example, from entering the through-hole 240 from between the two wheels 222 and 224.

[0238] In Figure 13, when the output shaft 204 starts rotating at high speed, the current supply from the battery 146 (see Figure 8) to the electromagnetic coil 110 is stopped. However, as described above, since the turbine wheel 224 is already rotating at high speed, the rotating shaft 40 rotates at high speed together with the turbine wheel 224 and the output shaft 204. At this time as well, for the same reasons as described above, sufficient rotational torque is transmitted from the output shaft 204 to the rotating shaft 40.

[0239] In Figure 3, it is preferable that the rotation direction of the output shaft 204 and the rotating shaft 40 is opposite to the rotation direction when the small cap nut 58, the large cap nut 60, and the male threaded portion 252 are screwed together. In this case, loosening of the small cap nut 58, the large cap nut 60, and the male threaded portion 252 during the rotation of the rotating shaft 40 is avoided. Alternatively, a mechanism to prevent loosening may be provided on the small cap nut 58, the large cap nut 60, or the male threaded portion 252.

[0240] Since the rotating shaft 40 holds the permanent magnet 72, an alternating current is generated in the electromagnetic coil 110 surrounding the permanent magnet 72. The alternating current is sent to the current converter 150 shown in Figures 1 and 8 via the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443. The conversion circuit 152 of the current converter 150 converts this alternating current into a direct current. When the 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, it supplies a direct current to the battery 146 (see Figure 8) via the capacitor 154. This charges the battery 146.

[0241] During this process, the current converter 150, particularly the conversion circuit 152 and the capacitor 154, becomes heated. However, in this embodiment, the conversion circuit 152 and the capacitor 154 inside the equipment case 158 are in close proximity to the cooling jacket 24. Therefore, the heat from the conversion circuit 152 and the capacitor 154 is quickly conducted to the cooling medium inside the cooling jacket 24. This prevents the conversion circuit 152 and the capacitor 154 from becoming excessively hot.

[0242] The electromagnetic coil 110 generates heat as current flows through it. As described above, the stator 36 is in contact with the second cooling oil. Therefore, the stator 36 is cooled by the second cooling oil. In addition, a cooling medium flows through the cooling jacket 24 provided in the main housing 16. The rotating electric machine 12 is rapidly cooled by this cooling medium. This also allows a predetermined magnetic force to be generated in the alternating magnetic field formed between the permanent magnet 72 and the electromagnetic coil 110.

[0243] 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, V-phase terminal 1442, and W-phase terminal 1443 are provided separately. Therefore, the heat generated in the stator 36 inside the main housing 16 is less likely to affect the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 inside the first casing 26. When power is applied, the electrical contacts between the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 and the U-phase coil, V-phase coil, and W-phase coil also generate heat. However, these electrical contacts are quickly cooled by the second cooling oil that flows into the contact chamber 290.

[0244] In this way, the electrical terminals (U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443), the electromagnetic coil 110, and the permanent magnet 72 are cooled, thus preventing heat from affecting the output control of the rotating electric machine system 10. Furthermore, the excitation of the electromagnetic coil 110 and the permanent magnet 72, etc., from decreasing due to heat is also prevented. As a result, the reliability of the rotating electric machine system 10 is improved.

[0245] Furthermore, since the main housing 16 that houses the rotating electric machine 12 and the first casing 26 that houses the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 are provided separately, the rotating electric machine 12 and the electrical terminal section are spaced apart from each other. As a result, the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 are less susceptible to vibrations generated as the rotor 34 rotates. In other words, the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 are protected from vibrations. Also, as described above, the occurrence of seizure in the first bearing 74 and the second bearing 84 is suppressed by the lubricating oil. Therefore, the rotating electric machine system 10 has excellent durability.

[0246] As the rotating electric machine 12 generates heat, heat is transferred to the partition member 410. This causes the partition member 410 to undergo thermal expansion. Here, both end faces in the axial direction of the partition member 410 are non-contact surfaces that do not come into contact with any other members. In other words, both end faces 410a and 410b in the axial direction of the partition member 410 are unconstrained surfaces that are not constrained by any other members. Therefore, both ends of the partition member 410 can freely expand along the axial direction of the partition member 410 due to thermal expansion. This prevents the ends of the thermally expanded partition member 410 from receiving compressive stress from other members.

[0247] The partition member 410 has relatively low strength due to its thin wall. Furthermore, if the partition member 410 is made of ceramics, it becomes brittle. However, as described above, compressive stress on the partition member 410 when thermal expansion occurs is avoided. Therefore, even if the partition member 410 is made of a highly brittle material, concerns about damage to the partition member 410 due to thermal expansion can be eliminated.

[0248] 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, which is fitted onto the left end 422 of the inner shaft 42, rotates integrally with the rotating shaft 40. As a result, the electrical signal generated in the resolver stator 130 is transmitted to the receiver via the transmission connector 136. The receiver, having read the electrical signal, calculates the rotation angle of the rotating shaft 40 based on the electrical signal. The receiver sends the calculation result to a control device (not shown). The control device calculates the rotation speed based on this rotation angle.

[0249] The resolver 132 is positioned on the protruding tip 46 of the rotating shaft 40, which is exposed from the rotating electric machine housing 14. Therefore, the resolver 132 is less affected by the heat generated in the electromagnetic coil 110 of the stator 36 inside the rotating electric machine housing 14. Furthermore, the resolver 132 is less affected by vibrations generated as the rotor 34 rotates. In addition, the first bearing 74 and the second bearing 84 that support the rotating shaft 40 are located inside the rotating electric machine housing 14. Therefore, the vibration of the first bearing 74 and the second bearing 84 is suppressed by the rotating electric machine housing 14. This also makes it difficult for vibrations to affect the resolver 132.

[0250] As described above, in this embodiment, the transmission of heat and vibration to the resolver 132 is suppressed. This results in more accurate detection of the rotation angle by the resolver 132. Furthermore, the lifespan of the resolver 132 is extended.

[0251] It may be necessary to replace resolver 132 with another resolver having a larger inner and outer diameter. If a single solid rotating shaft is used as the rotating shaft, replacing it with a resolver with a larger inner and outer diameter requires replacing it with a larger diameter solid rotating shaft. In this case, it is not easy to pass the larger diameter solid rotating shaft through the first bearing 74 and the second bearing 84.

[0252] In this embodiment, the rotating shaft 40 is composed of an outer shaft 44 and an inner shaft 42. The outer shaft 44 passes through the first bearing 74 and the second bearing 84, and a 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 with a larger inner and outer diameter, this can be done by replacing the inner shaft 42 with an inner shaft having a larger diameter at its 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.

[0253] In this embodiment, a third sub-branch 941 and a fourth sub-branch 942 are provided. Alternatively, the first air branch L may be branched into a first sub-branch and a second sub-branch. In this case, a portion of the first divided air is supplied from the first sub-branch to the first distal end 781, and a portion of the first divided air is supplied from the second sub-branch to the first proximal end 782. Alternatively, the first air branch L may be branched into a first sub-branch and a second sub-branch, and a third sub-branch 941 and a fourth sub-branch 942 may be provided.

[0254] In the gas turbine engine 200, the compressor wheel 222 and the turbine wheel 224 can be arranged in the opposite configuration to that shown in Figure 13. In this case, a through hole 240 can be formed in the turbine wheel 224, and an output shaft 204 can be provided in the compressor wheel 222. In addition, the compressor wheel 222 and the turbine wheel 224 may be of the centrifugal or axial flow type. If the compressor wheel 222 and the turbine wheel 224 are arranged on the same axis, a combination of a centrifugal and an axial flow type multi-stage compressor wheel and a multi-stage turbine wheel is also acceptable.

[0255] In Figure 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 the electromagnetic coil 110 is energized. In this case, the U-phase terminal 1441, V-phase terminal 1442, and W-phase terminal 1443 become electrical terminals that receive power from the battery 146.

[0256] The rotating electric machine system 10 can also be separated from the gas turbine engine 200 and used independently. If it is necessary to supply compressed air to the rotating electric machine system 10, a compression pump 320 may be provided outside the rotating electric machine housing 14, as shown in Figure 15, and this compression pump 320 may be used as an air supply device.

[0257] In this case, for example, the compression pump 320 is connected to at least one of the flexible tubes 470a to 470c. In this case, compressed air supplied from the compression pump 320 flows into the flexible tubes 470a to 470c. Also, a connecting hole 324 connected to the upstream communication hole 164 is formed in the second sub-housing 20. The connecting hole 324 is closed with a plug 326. In this state, compressed air is obtained by the compression pump 320 compressing the atmosphere or the like. This compressed air is supplied to the first hollow tube section 1601 to the third hollow tube section 1603.

[0258] Furthermore, in the above embodiment, the first cooling oil is circulated in the direction from the first bearing 74 to the second bearing 84, but conversely, the first cooling oil may be circulated in the direction from the second bearing 84 to the first bearing 74. In this case, the second sub-oil passage 181 is branched from the third sub-oil passage 188. Also, it is preferable to increase the outer diameter of the outer shaft 44 as it moves from the second bearing 84 to the first bearing 74. The disc portion 392 is provided at the second end of the first inner stopper 82.

[0259] As shown in Figure 16, it is also possible to provide a second circulation pump 412. In this case, a branch line 414 is provided upstream of the tank 318 in the first oil supply line 304. Alternatively, the branch line 414 may be provided downstream of the tank 318. The second circulation pump 412 is interposed between the branch line 414 and the second oil supply line 310.

[0260] In this configuration, a portion of the lubricating oil that flows out of the gas-liquid separator 302 is drawn out by the second circulation pump 412 and flows into the branch line 414. The lubricating oil (second cooling oil) in the branch line 414 flows through the second oil supply line 310, the input pipe section 314, the stator chamber 23, the output pipe section 316, and the second oil recovery line 312, and returns to the gas-liquid separator 302. This circulation and supply is then repeated.

[0261] There are no devices or components inside the rotating electric machine housing 14 that receive both the second cooling oil and compressed air simultaneously. Therefore, there is no particular need to return the second cooling oil to the gas-liquid separator 302. Thus, a bypass line 416 connecting the second oil recovery line 312 and the second oil supply line 310 may be provided. In this configuration, the second cooling oil flows into the branch line 414 via the bypass line 416. The second cooling oil then flows back into the bypass line 416 via the second oil supply line 310, the input pipe section 314, the stator chamber 23, the output pipe section 316, and the second oil recovery line 312.

[0262] As shown in Figure 17, it is also possible to circulate the second coolant in the opposite direction to that shown in Figure 11. In this case, the second coolant is input from the output pipe section 316 to the stator chamber 23 (oil passage inside the housing), and the second coolant is output from the stator chamber 23 to the input pipe section 314. The second coolant flows through the stator chamber 23 from the first bearing 74 to the second bearing 84. In other words, in this case, the direction of flow of the second coolant in the oil passage inside the housing is the first direction.

[0263] As described above, this embodiment is a rotating electric machine system (10) comprising a rotating electric machine (12) having a rotor (34) and a stator (36), and a rotating electric machine housing (14) housing the rotating electric machine, wherein the rotor has a rotating shaft (40) and a permanent magnet (72) provided on the rotating shaft, and the rotating electric machine system comprises a first bearing (74) and a second bearing (84) interposed between the rotating electric machine housing and the rotating shaft, and the rotating shaft In the diametrical direction, a cylindrical partition member (410) interposed between the rotor and the stator; a rotor chamber (22) formed radially inside the partition member and housing the rotor; an internal oil passage (23) formed radially outside the partition member and housing the stator; a first sealing member (453) that seals the space between the outer peripheral wall at the first axial end of the partition member and the rotating electric machine housing; the outer peripheral wall at the second axial end of the partition member and the rotating electric machine housing The present invention discloses a rotating electric machine system comprising: a second sealing member (464) that seals the space between the first bearing and the second bearing; and an oil circulation supply device that circulates and supplies lubricating oil to the first bearing, the second bearing and the oil passage inside the housing, wherein the oil circulation supply device has a first oil supply line (304), a second oil supply line (310), a first oil recovery line (305), and a second oil recovery line (312), the oil circulation supply device supplies the lubricating oil to the first bearing and the second bearing via the first oil supply line and supplies the lubricating oil to the oil passage inside the housing via the second oil supply line, the oil circulation supply device recovers the lubricating oil supplied to the first bearing and the second bearing via the first oil recovery line and recovers the lubricating oil that has flowed through the oil passage inside the housing via the second oil recovery line, and at least one of the axial end faces (410a, 410b) of the partition wall member is a non-contact surface that does not come into contact with any other member.

[0264] As described above, at least one of the two end faces of the partition member in the axial direction is a non-contact surface that does not come into contact with any other member. In other words, at least one of the two end faces is an unrestrained surface that is not constrained by any other member. Therefore, when the rotating electric machine heats up due to continuous operation, both ends of the partition member can freely expand along the axial direction of the partition member due to thermal expansion.

[0265] Therefore, compressive stress is avoided at both ends of the bulkhead member, which has expanded due to thermal expansion, from other members. In other words, the concentration of compressive stress at both ends of the bulkhead member is avoided. This eliminates concerns about damage to the bulkhead member.

[0266] This embodiment discloses a rotating electric machine system in which the rotating electric machine housing has an annular holder (460) surrounding the second end of the partition member, an annular guide (466) is arranged on the inner circumference side of the partition member, and the second end of the partition member is sandwiched between the annular guide and the annular holder.

[0267] The provision of an annular guide makes it easier to move the partition wall member inserted between the stator and rotor when assembling a rotating electric machine system. This is because the second end of the partition wall member can be guided along the annular guide. Therefore, the axial second end of the partition wall member can be easily positioned in a predetermined location where it is sealed by the second sealing member.

[0268] This embodiment discloses a rotating electric machine system in which the partition wall member is made of ceramics.

[0269] Ceramics are generally high-strength, insulating, and heat-resistant materials. Therefore, even when partition members are formed with thin walls, their strength and insulating properties are ensured, and they exhibit thermal stability. This results in sufficient durability for the partition members. Furthermore, even when ceramic partition members are interposed between the rotor and stator, the alternating magnetic field is hardly obstructed.

[0270] This embodiment discloses a rotating electric machine system in which the rotating electric machine housing comprises: a first oil supply passage that supplies the lubricating oil that has flowed through the first oil supply line to the first bearing and the second bearing; a first oil recovery passage that sends the lubricating oil supplied to the first bearing and the second bearing to the first oil recovery line; a second oil supply passage (314) that supplies the lubricating oil that has flowed through the second oil supply line to the internal oil passage of the housing; and a second oil recovery passage (316) that sends the lubricating oil supplied to the internal oil passage of the housing to the second oil recovery line.

[0271] In other words, in this case, a first oil supply passage, a first oil recovery passage, a second oil supply passage, and a second oil recovery passage are provided within the rotating electric machine housing. With this configuration, it is easy to separately provide a passage for lubricating oil supplied to and recovered from the bearings, and a passage for lubricating oil supplied to and recovered from the oil passages within the housing.

[0272] This embodiment discloses a rotating electric machine system in which the first oil supply passage has a first oil branch passage (N) leading to the first bearing and a second oil branch passage (R) leading to the second bearing.

[0273] With this configuration, it is easy to divert a portion of the lubricating oil flowing to the first bearing and send it to the second bearing as lubricating oil for the second bearing.

[0274] This embodiment discloses a rotating electric machine system in which the first oil recovery path includes a first oil guide (184) that guides the lubricating oil supplied from the first oil branch path to the first bearing to the oil circulation supply device, and a second oil guide (196) that guides the lubricating oil supplied from the second oil branch path to the second bearing to the oil circulation supply device.

[0275] This configuration allows the lubricating oil supplied to the first and second bearings, as well as the lubricating oil used to cool the stator, to be easily recovered and then resupplied to the first bearings, the second bearings, and the oil passages within the housing.

[0276] This embodiment discloses a rotating electric machine system comprising a gas supply device (200) that supplies gas to the first bearing and the second bearing, the rotating electric machine housing having gas supply passages (1601-1603) that supply the gas supplied from the gas supply device to the first bearing and the second bearing, and a gas discharge passage (173) that discharges the gas from the first bearing and the second bearing, and an oil circulation supply device that recovers the gas that has flowed through the gas discharge passage and the first oil recovery line, and the lubricating oil that has flowed through the first oil recovery line, and resupplies the lubricating oil from the first oil supply line to the first bearing and the second bearing, and resupplies it from the second oil supply line to the oil passage inside the housing.

[0277] The gas supplied to the first and second bearings forms a gas curtain. This gas curtain seals the lubricating oil supplied to the first and second bearings. In other words, the lubricating oil supplied to the first and second bearings is blocked by the gas curtain. Therefore, the lubricating oil is prevented from splashing around the first or second bearing. This prevents, for example, the rotating shaft from becoming contaminated with lubricating oil.

[0278] Furthermore, since the oil circulation supply system recovers both gas and lubricating oil together, there is no need to recover the gas and lubricating oil separately. Consequently, there is no need to install a gas recovery device in the rotating electric machine system. This avoids complicating the configuration of the rotating electric machine system.

[0279] This embodiment discloses a rotating electric machine system in which the oil circulation supply device includes a gas-liquid separator (302) for separating the gas and the lubricating oil.

[0280] Since the gas-liquid separator separates the gas and the lubricating oil, only the lubricating oil can be resupplied to the first oil supply line and the second oil supply line, even though the gas and the lubricating oil are recovered together. That is, in this case, it is easy to circulate and supply the lubricating oil to the first bearing, the second bearing, and the oil passage in the housing.

[0281] This embodiment discloses a compound power system (500) including the above-described rotating electrical machine system (10) and an internal combustion engine (200) having an output shaft (204) that rotates integrally with the rotating shaft (40).

[0282] Thereby, a compound power system in which the rotating electrical machine system and the internal combustion engine are integrally combined can be configured. In this case, even though the stator in the rotating electrical machine system is cooled as described above, it is possible to avoid the complication or enlargement of the rotating electrical machine system. Therefore, it is possible to avoid the complication or enlargement of the compound power system. Also, an increase in the weight of the compound power system is avoided.

[0283] Note that the present invention is not limited to the above-described disclosure, and various configurations can be adopted without departing from the gist of the present invention.

Explanation of Reference Numerals

[0284] 10... Rotating electrical machine system 12... Rotating electrical machine 14... Rotating electrical machine housing 16... Main housing 18... First sub-housing 20... Second sub-housing 22... Rotor chamber 23... Stator chamber 24... Cooling jacket 26... First casing 28... Second casing 34... Rotor �6... Stator 40... Rotating shaft 42... Inner shaft 44... Outer shaft 70... Cylindrical member 72... Permanent magnet 74... First bearing 78... First insertion hole 80... First bearing holder 81... First outer stopper 82...First internal stopper 84...Second bearing 86...Second insertion hole 88...Second bearing holder 90...Second internal stopper 92...Second external stopper 96...Rectifier component 110...Electromagnetic coil 110a...Terminal wire 112...Insulating substrate 132…Resolver 146…Battery 148...Thermistor 154...Capacitor 156...Control circuit 162...Collection channel 164…Upstream communication hole 166…Air relay path 172... Exhaust passage 174... Input passage 176...Main oil path 178...1st inflow hole 180...1st sub-oilway 181...2nd sub-oilway 182...First oil supply port 184...First drain channel 186…Oil receiving hole 188…3rd sub-oil passage 190...Oil outflow hole 195...Second oil supply hole 196...Second drain passage 197...Second drain hole 198...First drain hole 200...Gas turbine engine 202…Engine housing 204…Output shaft 214... Intake space 216... Extraction passage 217...Air vent hole 218...Engaging recess 220... Shroud case 222... Compressor wheel 224... Turbine wheel 226... Diffuser 228... Combustor 234... Vent 236... Chamber 274... Combustion air passage 275…Fuel supply nozzle 276…Intermediate port 280…Exhaust port 290…Contact chamber 291... Terminal chamber 294... Blocking protrusion 295... Terminal part 296... Screw 302...Gas-liquid separation device 304...First oil supply line 305...First oil recovery line 306...Exhaust line 308…Circulation pump 310…Second oil supply line 312…Second oil recovery line 314…Input pipe section 316…Output pipe section 318…Tank 320…Compression pump 340…Oil receiving recess 350…Inner oil guide member 354…Inner oil passage in rotor 356…First magnet stopper 358…Second magnet stopper 385…Annular gap 386…First oil supply passage 392…Disk section 410…Partition member 412…Second circulation pump 414…Branch line 416…Bypass line 450…Starting path 453…First seal member 454…Inner peripheral side oil passage in stator 456…Inner annular protrusion 458…Outer annular protrusion 460…Annular holder 464…Second seal member 466…Annular guide 468…Third seal member 470a~470c…Flexible tube 500…Compound power system 781…First distal end 782…First proximal end 861…Second distal end 862…Second proximal end 941…Third sub-branch path 942…Fourth sub-branch path 943…Outlet path 1441…U-phase terminal 1442…V-phase terminal 1443…W-phase terminal 1601…First hollow pipe section 1602…Second hollow pipe section 1603…Third hollow pipe section 3582…Second oil supply passage L…First air branch path M…Second air branch path N…First oil branch path R…Second oil branch path

Claims

1. A rotating electric machine system comprising a rotating electric machine having a rotor and a stator, and a rotating electric machine housing that houses the rotating electric machine, The rotor comprises a rotating shaft and a permanent magnet provided on the rotating shaft. The aforementioned rotating electric machine system includes a first bearing and a second bearing interposed between the rotating electric machine housing and the rotating shaft, In the diametrical direction of the rotating shaft, a cylindrical partition member is interposed between the rotor and the stator, A rotor chamber is formed radially inward of the partition wall member and houses the rotor, An oil passage is formed radially outward of the partition wall member and houses the stator within the housing, A first sealing member seals the outer peripheral wall at the first axial end of the partition wall member and the rotating electric machine housing, An annular holder surrounding the outer peripheral wall at the second axial end of the partition wall member, A second sealing member is provided on the annular holder and seals the space between the outer peripheral wall at the second end of the partition member and the rotating electric machine housing, An annular guide is positioned on the inner circumference side of the second end of the partition wall member, A third sealing member is provided on the annular guide and seals the space between the inner circumferential wall at the second end of the partition member and the rotating electric machine housing, An oil circulation supply device that circulates and supplies lubricating oil to the first bearing, the second bearing, and the oil passage inside the housing, Equipped with, The oil circulation supply device includes a first oil supply line, a second oil supply line, a first oil recovery line, and a second oil recovery line. The oil circulation supply device supplies the lubricating oil to the first bearing and the second bearing via the first oil supply line, and supplies the lubricating oil to the oil passage inside the housing via the second oil supply line. The oil circulation supply device recovers the lubricating oil supplied to the first bearing and the second bearing via the first oil recovery line, and recovers the lubricating oil that has flowed through the oil passage inside the housing via the second oil recovery line. At least one of the two end faces in the axial direction of the partition wall member is a non-contact surface that does not come into contact with any member. A rotating electric machine system in which the second end of the partition member is sandwiched between the second sealing member and the third sealing member.

2. A rotating electric machine system according to claim 1, wherein the second end of the partition member is sandwiched between the annular guide and the annular holder.

3. A rotating electric machine system according to claim 1, wherein the partition wall member is made of ceramics.

4. In the rotating electric machine system according to claim 1, the rotating electric machine housing is A first oil supply passage supplies the lubricating oil that has flowed through the first oil supply line to the first bearing and the second bearing, A first oil recovery path that sends the lubricating oil supplied to the first bearing and the second bearing to the first oil recovery line, A second oil supply passage supplies the lubricating oil that has flowed through the second oil supply line to the oil passage inside the housing, A second oil recovery passage that sends the lubricating oil supplied to the oil passage inside the housing to the second oil recovery line, A rotating electric machine system having a rotating motor.

5. The rotating electric machine system according to claim 4, wherein the first oil supply passage comprises a first oil branch passage leading to the first bearing and a second oil branch passage leading to the second bearing.

6. In the rotating electric machine system according to claim 5, the first oil recovery path is A first oil conduit guides the lubricating oil supplied from the first oil branch to the first bearing to the oil circulation supply device, A rotating electric machine system having a second oil conduit that guides the lubricating oil supplied from the second oil branch to the second bearing to the oil circulation supply device.

7. A rotating electric machine system according to any one of claims 1 to 6, comprising a gas supply device for supplying gas to the first bearing and the second bearing, The rotating electric machine housing has a gas supply passage for supplying the gas supplied from the gas supply device to the first bearing and the second bearing, and a gas discharge passage for discharging the gas from the first bearing and the second bearing. The oil circulation supply device recovers the gas that has flowed through the gas discharge passage and the first oil recovery line, and the lubricating oil that has flowed through the first oil recovery line, and resupplies the lubricating oil from the first oil supply line to the first bearing and the second bearing, and resupplies it from the second oil supply line to the oil passage inside the housing, in a rotating electric machine system.

8. The rotating electric machine system according to claim 7, wherein the oil circulation supply device includes a gas-liquid separator for separating the gas and the lubricating oil.

9. The rotating electric machine system according to claim 1, wherein the second seal member and the third seal member are positioned to be offset from each other in the axial direction of the partition wall member and to partially overlap in the radial direction.

10. A combined power system comprising the rotating electric machine system described in claim 1 and an internal combustion engine having an output shaft that rotates integrally with the rotating shaft.

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