Rotary electric machine system

Abstract

To prevent leakage of a liquid refrigerant.SOLUTION: A rotor 62 of a rotary electric machine system comprises: a sleeve 220 which covers a rotary shaft; and a collar 240 arranged on an outer periphery of the sleeve 220 and the rotary shaft. An internal space 242 is formed between the rotary shaft and the collar 240. In the sleeve 220, a communication flow channel 232 which communicates a flow channel 210 in the rotor with the internal space 242 is formed in an insertion part 224 which is inserted into the internal space 242. An outer peripheral surface of the insertion part 224 comprises an abutting surface 230 on which an inner peripheral surface 256 of the collar 240 abuts. The sleeve 220 comprises: an entrance 234 from the flow channel 210 in the rotor to the communication flow channel 232; and an exit 236 from the communication flow channel 232 to the internal space 242. The entrance 234 and the exit 236 are located inward than the contact surface 230 in a diameter direction of the rotary shaft.SELECTED DRAWING: Figure 5

Description

[Technical Field]

[0001] The present invention relates to a rotating electric machine system including a rotating electric machine having a rotor and a stator, and a housing that accommodates the stator. [Background technology]

[0002] A rotating electric machine includes a rotor having a rotating shaft and a stator positioned on the outer periphery of the rotor. The rotor has permanent magnets held by the rotating shaft. When the rotating shaft rotates, an induced current is generated in the electromagnetic coils that make up the stator. In this case, the rotating electric machine functions as a generator.

[0003] When an induced current continues to flow through an electromagnetic coil, the electromagnetic coil becomes hot. As a result, the permanent magnets are subject to radiant heat. Furthermore, when the rotating shaft rotates at high speed, the rotor experiences significant air resistance. For these reasons, the temperature of the permanent magnets rises. As the temperature of the permanent magnets approaches their Curie temperature, the magnetic force of the permanent magnets decreases.

[0004] Patent Document 1 proposes a configuration in which a refrigerant supply passage is formed inside the hollow interior of a rotating shaft, and a refrigerant flow space is formed between the rotating shaft and a rotor core. The rotor core is positioned and fixed to the rotating shaft via two retainers. The rotating shaft has a communication passage formed along its diameter. Each of the two retainers is also provided with a refrigerant discharge port.

[0005] A coolant is supplied to the coolant supply passage. The coolant then moves to the outer circumferential surface of the rotating shaft via a communication passage, and then flows through the coolant flow space. The coolant is discharged to the outside of the rotor (the hollow interior of the housing) via a coolant outlet. The coolant flows toward the stator. Patent Document 1 lists cooling oil as an example of the coolant. [Prior art documents] [Patent documents]

[0006] [Patent Document 1] Japanese Patent Application Laid-Open No. 2011-97784 Summary of the Invention [Problem to be solved by the invention]

[0007] It is undesirable for the coolant to leak to any location other than the normal outlet.

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

[0009] An aspect of the present disclosure is a rotating electric machine system including a rotating electric machine having a rotor and a stator, and a housing that accommodates the stator.

[0010] The rotor includes a rotating shaft, a sleeve that covers the rotating shaft from an outer circumferential side, a permanent magnet held by the sleeve, a collar disposed on the outer circumferential side of the sleeve and the rotating shaft, an internal rotor flow path formed between the outer circumferential surface of the rotating shaft and the inner circumferential surface of the sleeve and including an annular space extending along the axial direction of the rotating shaft, and an internal space formed between the outer circumferential surface of the rotating shaft and the inner circumferential surface of the collar. The rotating electric machine system includes a liquid refrigerant supply device that supplies liquid refrigerant to the internal rotor flow path. The sleeve includes an insertion portion that is at one axial end of the sleeve and is inserted into the internal space and separates the internal rotor flow path from the internal space, and a communication flow path formed in the insertion portion that communicates the internal rotor flow path with the internal space. The outer circumferential surface of the insertion portion includes an abutment surface that abuts the inner circumferential surface of the collar.

[0011] In the above configuration, an inlet through which the liquid refrigerant flows from the rotor internal flow path into the communicating flow path and an outlet through which the liquid refrigerant flows from the communicating flow path into the internal space are located inward of the abutment surface in the diameter direction of the rotating shaft. [Effects of the Invention]

[0012] According to the present invention, it is possible to prevent liquid refrigerant from leaking from between the contact surface, which is a part of the outer peripheral surface of the sleeve, and the inner peripheral surface of the collar that contacts the contact surface. [Brief explanation of the drawings]

[0013] [Figure 1] FIG. 1 is a schematic overall perspective view of a compound power system including a rotating electrical machine system according to an embodiment of the present invention. [Figure 2] FIG. 2 is a schematic cross-sectional side view of the rotating electrical machine system as viewed from a direction perpendicular to the axial direction. [Figure 3] FIG. 3 is a schematic cross-sectional side view of the rotating electrical machine system as seen from a direction perpendicular to the axial direction, at a rotation angle different from that in FIG. [Figure 4] FIG. 4 is an enlarged cross-sectional view of a main part around the first bearing. [Figure 5] FIG. 5 is an enlarged cross-sectional view of a main part around the second bearing. [Figure 6] FIG. 6 is a schematic perspective view of one end (second end) of the sleeve in the axial direction. [Figure 7] FIG. 7 is a schematic flow diagram showing the flow paths of the gas refrigerant and the liquid refrigerant. DETAILED DESCRIPTION OF THE INVENTION

[0014] In the following description, compressed air AR (see FIGS. 2 and 7) is exemplified as a gas refrigerant, and cooling oil CO1 and cooling oil CO2 (see FIGS. 2, 3, and 7) are exemplified as liquid refrigerants. In this embodiment, the cooling oil CO1 and cooling oil CO2 are supplied from the same oil supply device 904 (see FIG. 7) as the lubricating oil LO supplied to the first bearing 400 and the second bearing 500. However, this is merely an example. The gas refrigerant may be compressed nitrogen or the like. The liquid refrigerant may be oil supplied from an oil supply device separate from the oil supply device 904. Alternatively, the liquid refrigerant may be an organic solvent with a high boiling point and low volatility.

[0015] 1 is a schematic overall perspective view of a combined power system 10. The combined power system 10 includes a rotating electric machine system 20 according to this embodiment and a gas turbine engine 950. The axis of the rotating electric machine system 20 and the axis of the gas turbine engine 950 coincide with each other. In other words, the rotating electric machine system 20 and the gas turbine engine 950 are arranged in series on the same axis.

[0016] The combined power system 10 is used as a propulsion power source in, for example, an air vehicle, a ship, or an automobile. Specific examples of suitable air vehicles include drones and multicopters. When mounted on an air vehicle, the combined power system 10 is used as a power drive source for rotating, for example, a propeller or a ducted fan. When mounted on a ship, the combined power system 10 is used as a rotational force generator for a screw. When mounted on an automobile, the combined power system 10 is used as a power drive source for rotating a motor.

[0017] The combined power system 10 can also be used as a power source for auxiliary power supplies in aircraft, ships, buildings, etc. In addition, the combined power system 10 can also be used as a gas turbine power generation facility.

[0018] The gas turbine engine 950 is an internal combustion engine. The gas turbine engine 950 is also a gas refrigerant supply device that supplies compressed air AR. As will be described later, the compressed air AR circulates within the rotating electrical machine housing 22 as a gas refrigerant.

[0019] In the following description, "left," "right," "bottom," and "top" refer to the left, right, bottom, and top directions in Figures 2 and 3, respectively. However, these directions are merely used for convenience to simplify the description and make it easier to understand. In other words, the directions described in the specification are not necessarily the directions when the combined power system 10 is actually used.

[0020] In the following description, the left end in the axial direction of each of the rotating electrical machine system 20 and the gas turbine engine 950 may be referred to as a first end. The right end in the axial direction of each of the rotating electrical machine system 20 and the gas turbine engine 950 may be referred to as a second end. Furthermore, in each member, the surface facing the first end may be referred to as a "first end face," and the surface facing the second end may be referred to as a "second end face."

[0021] The rotating electric machine system 20 will now be described. Figures 2 and 3 are schematic side cross-sectional views of the rotating electric machine system 20 as viewed from a direction perpendicular to the axial direction. Note that the rotation angles of the rotating electric machine system 20 differ between Figures 2 and 3. The rotating electric machine system 20 includes a rotating electric machine 60 and a rotating electric machine housing 22 (housing) that houses the rotating electric machine 60. In this embodiment, the rotating electric machine 60 is a generator.

[0022] The rotating electrical machine housing 22 has a main housing 24, a first sub-housing 26, and a second sub-housing 28. The first and second ends of the main housing 24 are open ends, and the main housing 24 has a generally cylindrical shape. The first sub-housing 26 is connected to the first end (left open end) of the main housing 24. The second sub-housing 28 is connected to the second end (right open end) of the main housing 24. As a result, the first and second ends of the main housing 24 are closed.

[0023] 1, a first casing 40 and a second casing 42 are provided on the outer circumferential surface of the main housing 24. The first casing 40 and the second casing 42 will be described later.

[0024] A cooling jacket 38 is formed inside the side periphery of the main housing 24. A cooling medium such as cooling water flows through the cooling jacket 38.

[0025] 2 and 3, the main housing 24 has a hollow interior 30. The hollow interior 30 is divided into a rotor chamber 34 and a stator chamber 36 by a partition member 32. The rotor chamber 34 is a chamber formed on the inside (inner peripheral side) of the partition member 32 in the diameter direction. The stator chamber 36 is a chamber formed on the outside (outer peripheral side) of the partition member 32 in the diameter direction.

[0026] The rotating electric machine 60 includes a rotor 62 and a stator 64 that surrounds the outer periphery of the rotor 62. The partition member 32 is interposed between the rotor 62 and the stator 64 in the radial direction of the rotating shaft 66. Therefore, the rotor 62 is located on the inner periphery side of the partition member 32. In other words, the rotor 62 is housed in the rotor chamber 34. The stator 64 is located on the outer periphery side of the partition member 32. In other words, the stator 64 is housed in the stator chamber 36.

[0027] The partition member 32 is, for example, a cylindrical body made of insulating, non-magnetic ceramics. The distance between the outer peripheral surface of the permanent magnet 270 that constitutes the rotor 62 and the inner peripheral surface of the partition member 32 is preferably greater than the distance between the outer peripheral surface of the partition member 32 and the plurality of electromagnetic coils 310 that constitute the stator 64. The former is preferably about 2.5 to 4 times the latter. As an example of a combination of the former and latter, the former is in the range of 1.1 mm to 2.1 mm, and the latter is in the range of 0.3 mm to 0.5 mm.

[0028] A first end of the partition member 32 is inserted into a cylindrical portion 620 that protrudes axially from a first wall surface 612 of the partition member 610. The inner surface of the stator chamber 36 includes the first wall surface 612 of the partition member 610, the outer peripheral surface of the partition member 32, and the inner peripheral surface of the main housing 24. In other words, the first wall surface 612 of the partition member 610 forms part of the inner surface of the stator chamber 36. The rotor chamber 34 and the stator chamber 36 are liquid-tightly and airtightly separated by the partition member 32, the partition member 610, and the inner peripheral surface of the main housing 24. In other words, the rotor chamber 34 and the stator chamber 36 are spaces independent of each other.

[0029] The rotor 62 is configured to include a rotating shaft 66, a sleeve 220, and a permanent magnet 270. The sleeve 220 has an inner hole 222 that extends along the axial direction of the sleeve 220. The rotating shaft 66 is passed through the inner hole 222. Therefore, the sleeve 220 is interposed between the rotating shaft 66 and the permanent magnet 270 in the radial direction of the rotating shaft 66. A main portion of an in-rotor flow path 210, which will be described later, is formed by the inner hole 222 and the rotating shaft 66.

[0030] The rotating shaft 66 has an inner shaft 68 and a hollow cylindrical outer shaft 70. Both ends of the outer shaft 70 are open. That is, as shown in FIG. 2, the outer shaft 70 has a first hollow end 72 and a second hollow end 74.

[0031] The inner shaft 68 is removably inserted into the outer shaft 70. The inner shaft 68 is longer than the outer shaft 70. As shown in Fig. 2, the inner shaft 68 has a left end 80 (end on the first end side) which is one end in the axial direction, and a right end 82 (end on the second end side) which is the other end in the axial direction.

[0032] A portion of the left end portion 80 is exposed from the first hollow end portion 72 of the outer shaft 70. Hereinafter, the portion of the left end portion 80 exposed from the first hollow end portion 72 will be referred to as an extension portion 90. The extension portion 90 is connected to the first hollow end portion 72 of the outer shaft 70 by a positioning and fixing portion 100 that includes a nut member 102 and the like.

[0033] The resolver rotor 52 and a lock nut 104 are provided at the extending tip of the extending portion 90. The lock nut 104 prevents the resolver rotor 52 from coming off the extending portion 90.

[0034] A first end of an output shaft 964 that constitutes a gas turbine engine 950 is connected to the right end 82 of the inner shaft 68, as will be described later.

[0035] The outer shaft 70 has a first shaft portion 70a to a fifth shaft portion 70e arranged in a direction from the first end to the second end. The outer diameters of the first shaft portion 70a to the fourth shaft portion 70d increase in stages. The outer diameter of the fifth shaft portion 70e is smaller than the outer diameter of the fourth shaft portion 70d and is approximately the same as the outer diameter of the third shaft portion 70c.

[0036] As shown in Fig. 4, the first shaft portion 70a has a first external thread 76. As shown in Figs. 3 and 4, the second shaft portion 70b has a plurality of groove-like flow paths 212 formed on its outer peripheral surface along the circumferential direction of the second shaft portion 70b. Fig. 4 shows one of the plurality of groove-like flow paths 212. Each of the plurality of groove-like flow paths 212 is recessed inward in the radial direction of the rotary shaft 66 from the outer peripheral surface of the second shaft portion 70b and extends along the axial direction of the rotary shaft 66.

[0037] The third shaft portion 70c has a cylindrical shape with a substantially constant inner diameter and outer diameter. A plurality of guide passages 214 are formed on the outer peripheral surface of the third shaft portion 70c along the circumferential direction of the third shaft portion 70c. FIG. 4 shows one of the plurality of guide passages 214. Each of the plurality of guide passages 214 is formed at a first end of the third shaft portion 70c facing the second shaft portion 70b. The first end of the guide passage 214 is connected to a second end of the groove-shaped passage 212. The guide passage 214 constitutes a part of the rotor internal passage 210 (described below). The guide passage 214 is inclined from the inner side toward the outer side (toward the outer peripheral surface of the third shaft portion 70c) in the diameter direction of the rotary shaft 66 as it moves away from the second shaft portion 70b.

[0038] 2 and 5, the fourth shaft portion 70d has on its outer circumferential surface a flange portion 77 and a second external thread 78. As shown in Figures 2, 3 and 5, the fifth shaft portion 70e has a cylindrical shape with substantially constant inner and outer diameters.

[0039] 2, 3, and 4, a screw cap 200 is screwed onto the first external thread 76 of the first shaft portion 70a. A second end face of the screw cap 200 abuts against a first end face of a first inner ring 402 of a first bearing 400 (see FIG. 4).

[0040] 2 and 3, most of the third shaft portion 70c is covered by the sleeve 220. In other words, the sleeve 220 covers the third shaft portion 70c, which constitutes the rotary shaft 66, from the outer periphery side.

[0041] Permanent magnets 270 are held in the sleeve 220. In this embodiment, the rotor 62 is a so-called SPM type in which the permanent magnets 270 are arranged on the outer circumferential surface of the sleeve 220. Alternatively, the rotor 62 may be a so-called IPM type in which the permanent magnets 270 are embedded in the sleeve 220.

[0042] The sleeve 220 and the permanent magnet 270 are sandwiched between the magnet stopper 272 and the collar 240 in the axial direction of the rotating shaft 66. This positions and fixes the sleeve 220 to the outer peripheral surface of the outer shaft 70. In other words, displacement of the sleeve 220 and the permanent magnet 270 with respect to the outer shaft 70 is prevented. In this way, the magnet stopper 272 and the collar 240 positions and fixes the permanent magnet 270 by positioning and fixing the sleeve 220.

[0043] 4, a portion of the magnetic stopper 272 is interposed between the inner peripheral surface of the guide member 560 and the outer peripheral surface of the inner ring stopper 460. In the axial direction of the rotating shaft 66, a first ring body 274 is sandwiched between the magnetic stopper 272 and the permanent magnet 270. In the axial direction of the rotating shaft 66, a second ring body 276 is sandwiched between the permanent magnet 270 and the collar 240.

[0044] The collar 240 is disposed on the outer peripheral side of the sleeve 220 and the fourth shaft portion 70d. An internal space 242 is formed between the outer peripheral surface of the fourth shaft portion 70d and the inner peripheral surface 256 of the collar 240. That is, the rotor 62 has the internal space 242. As shown in FIG. 5 , the insertion portion 224 of the sleeve 220 is inserted into the internal space 242. The insertion portion 224 is an end portion at the second end of the sleeve 220.

[0045] In the illustrated example, the insertion portion 224 has a first annular protrusion 226 and a second annular protrusion 228. The first annular protrusion 226 is a portion of the sleeve 220 that protrudes in an annular shape along the axial direction from a second end of a main body portion 225, which has constant inner and outer diameters. The first annular protrusion 226 has a smaller diameter than the main body portion 225. The second annular protrusion 228 is a portion that protrudes in an annular shape along the axial direction of the sleeve 220 from the second end of the first annular protrusion 226. The second annular protrusion 228 has a smaller diameter than the first annular protrusion 226.

[0046] The insertion portion 224 may be the second end of the main body portion 225. That is, it is not essential that the insertion portion 224 include the first annular protrusion 226 and the second annular protrusion 228.

[0047] An inner peripheral surface 256a of the first inner chamber 242a abuts against the outer peripheral surface of the first annular protrusion 226. The inner peripheral surface 256a of the first inner chamber 242a is part of the inner peripheral surface 256 of the collar 240. Hereinafter, the portion of the outer peripheral surface of the first annular protrusion 226 that abuts against the inner peripheral surface 256a of the collar 240 will be referred to as the abutment surface 230. In the illustrated example, the entire outer peripheral surface of the first annular protrusion 226 is the abutment surface 230. However, the abutment surface 230 may be part of the outer peripheral surface of the first annular protrusion 226.

[0048] The second annular protrusion 228 constituting the insertion portion 224 separates the rotor internal flow path 210 from the internal space 242. As shown in Figures 5 and 6, a communication flow path 232 is provided from the inner circumferential surface of the main body portion 225 to the first end of the second annular protrusion 228. There may be a single communication flow path 232 or multiple communication flow paths 232.

[0049] The rotor internal flow path 210 and the internal space 242 are connected to each other via the communicating flow path 232. An inlet 234 for the cooling oil CO2 to the communicating flow path 232 is formed on the inner circumferential surface of the main body 225, facing the rotor internal flow path 210. An outlet 236 for the cooling oil CO2 from the communicating flow path 232 is formed on the first end of the second annular protrusion 228, facing the internal space 242. The inlet 234 is located more inward than the outlet 236 in the radial direction of the rotating shaft 66. The outlet 236 is located more inward than the abutment surface 230 in the radial direction of the rotating shaft 66. Therefore, the outlet 236 is not formed on the abutment surface 230. Therefore, the entire abutment surface 230 abuts against the inner circumferential surface 256a of the first internal chamber 242a.

[0050] The communicating flow passage 232 is inclined from the inner side to the outer side in the diameter direction of the rotary shaft 66 as it approaches the internal space 242 from the rotor flow passage 210, in other words, as it moves from the inlet to the outlet. However, this is just one embodiment. The communicating flow passage 232 may also be L-shaped, having a portion extending along the axial direction.

[0051] The collar 240 has a cylindrical portion 244 and a partition wall 246. The partition wall 246 is formed in a disk shape inside the cylindrical portion 244. An insertion hole 248, through which the rotary shaft 66 is inserted, is formed at the center in the diameter direction of the partition wall 246. An internal thread 250 is formed on the inner peripheral surface of the insertion hole 248. A receiving hole 252 is connected to the first end side of the insertion hole 248. The internal diameter of the receiving hole 252 is larger than the internal diameter of the insertion hole 248. A flange portion 77 provided on the fourth shaft portion 70d of the outer shaft 70 engages with the receiving hole 252. The internal thread 250 is threadedly engaged with a second external thread 78 provided on the fourth shaft portion 70d. In this manner, the collar 240 is held on the outer shaft 70.

[0052] The partition wall 246 divides the internal space 242 into a first internal chamber 242a and a second internal chamber 242b. In the diameter direction of the partition wall 246, a discharge flow path 254 is formed on the outer periphery of the insertion hole 248. There may be a single discharge flow path 254 or multiple discharge flow paths 254. The first internal chamber 242a and the second internal chamber 242b communicate with each other through the discharge flow path 254. An inner peripheral surface 256a of the first internal chamber 242a abuts against the abutment surface 230 of the sleeve 220.

[0053] Next, the configuration around the first end of the rotor 62 will be described.

[0054] As shown in Figures 2, 3, and 4, the second shaft portion 70b of the outer shaft 70 is rotatably held in the first sub-housing 26 via a first bearing 400. Specifically, a first bearing chamber 410 is formed in the first sub-housing 26. A hollow cylindrical first bearing holder 420 and a hollow cylindrical holder spacer 450 are inserted into a first end of the first bearing chamber 410. The first bearing 400 is interposed between the second shaft portion 70b and the first bearing holder 420. A first end of the rotating shaft 66 is passed through a first inner ring 402 of the first bearing 400.

[0055] An insulating material 430 is interposed between the outer surface of the first outer ring 406 of the first bearing 400 and the inner surface of the first bearing holder 420. The insulating material 430 electrically insulates the first bearing 400 and the first bearing holder 420.

[0056] As shown in Fig. 4, an annular groove 422 is formed in the first bearing holder 420. A plurality of first oil supply holes 424 are formed radially within the annular groove 422. Furthermore, a plurality of communication holes 452 are formed radially within the holder spacer 450. The inner peripheral opening of each of the plurality of communication holes 452 overlaps with the outer peripheral opening of each of the plurality of first oil supply holes 424. The plurality of communication holes 452 and the plurality of first oil supply holes 424 are holes for supplying lubricating oil LO from an oil supply device 904 to the first bearing 400.

[0057] The first bearing holder 420 has a plurality of communication holes 426. The plurality of communication holes 426 are holes for discharging the lubricating oil LO supplied to the first bearing 400 to the outside of the first bearing holder 420.

[0058] A spacer ring 440 is positioned and fixed inside the first bearing holder 420. A preload member 442 made of a disc spring applies a load (preload) to the second end face of the first outer ring 406 via the spacer ring 440. The load is applied in the axial direction of the rotating shaft 66. An insulating material 444 is interposed between the second end face of the first bearing 400 and the first end face of the spacer ring 440.

[0059] The spacer ring 440 has a plurality of relay holes 446. Each relay hole 446 communicates with each first oil supply hole 424 via each communication hole 426.

[0060] An inner race stopper 460 is inserted into the first bearing holder 420. The first inner race 402 of the first bearing 400 is sandwiched between the screw cap 200 and the inner race stopper 460 in the axial direction of the outer shaft 70. This positions and fixes the first bearing 400 at a predetermined location on the outer peripheral surface of the outer shaft 70.

[0061] The left end of the first bearing chamber 410 is farther from the output shaft 964 than the right end of the first bearing chamber 410. Hereinafter, the left end of the first bearing chamber 410 that is farther from the output shaft 964 than the right end may be referred to as the "first distal end 412." Additionally, the right end that is closer to the output shaft 964 than the first distal end 412 may be referred to as the "first proximal end 414."

[0062] 2, a shaft hole 470 is formed in the diametric center of the resolver holder 56. The extending tip of the extension portion 90 passes through the shaft hole 470. At a first end of the resolver holder 56, the shaft hole 470 is closed by a cap cover 472.

[0063] The resolver stator 54 is held on the inner peripheral surface of the shaft hole 470. The resolver rotor 52 is located on the inner peripheral side of the resolver stator 54. The resolver 50 is composed of the resolver stator 54 and the resolver rotor 52.

[0064] An engagement hole 474 is formed in the resolver holder 56. The transmission connector 58 is engaged with the engagement hole 474. The resolver stator 54 and the transmission connector 58 are electrically connected via a signal line 59. The transmission connector 58 is a connector for transmitting a signal related to a rotation parameter to a receiver (not shown).

[0065] Next, a description will be given of the configuration around the second end of the rotor 62. As shown in Figures 2, 3 and 5, the second end of the rotary shaft 66 is rotatably held in the main housing 24 via a second bearing 500.

[0066] A retaining recess 508 is formed at the second end of the main housing 24, recessed toward the first end and communicating with the rotor chamber 34. A second bearing chamber 520 is formed by the retaining recess 508 of the main housing 24 and a hollow recess 512 of the hollow second sub-housing 28. The second bearing 500 is housed in the second bearing chamber 520.

[0067] The left end of the second bearing chamber 520 is farther from the output shaft 964 than the right end of the second bearing chamber 520. Hereinafter, the left end of the second bearing chamber 520 that is farther from the output shaft 964 than the right end may be referred to as the "second distal end 522." Additionally, the right end that is closer to the output shaft 964 than the second distal end 522 may be referred to as the "second proximal end 524."

[0068] The second bearing 500 is sandwiched between the outer peripheral surface of the second end of the outer shaft 70 and the inner peripheral surface of the second bearing holder 530. The second bearing holder 530 is connected to the second end of the main housing 24 via bolts or the like. This positions and fixes the second bearing holder 530 to the rotating electric machine housing 22.

[0069] The second bearing holder 530 is located radially outward of the second outer ring 506 and covers the second bearing 500 from the outer peripheral surface side of the second outer ring 506. An insulating material (not shown) is interposed between the outer peripheral surface of the second outer ring 506 and the inner peripheral surface of the second bearing holder 530.

[0070] An inner inner race stopper 540 and an outer inner race stopper 542 are inserted into the second bearing holder 530. The inner inner race stopper 540 is located at the second distal end 522, and the outer inner race stopper 542 is located at the second proximal end 524. The second inner race 502 of the second bearing 500 is sandwiched between the inner inner race stopper 540 and the outer inner race stopper 542. This positions and fixes the second bearing 500 at a predetermined location on the outer peripheral surface of the outer shaft 70.

[0071] A rectifying member 550 is housed in the hollow recess 512 of the second sub-housing 28. The rectifying member 550 has a generally truncated cone shape, and its diameter tapers from the first end to the second end. The second end of the rectifying member 550 is positioned and fixed to the second end of the main housing 24.

[0072] An air vent 554 is formed in the center in the diameter direction of the flow rectifying member 550. The inner peripheral surface of the air vent 554 faces the outer peripheral surface of the outer inner ring stopper 542 in the diameter direction.

[0073] 2, 3, 4, and 5, annular flow spaces 216 are formed in the screw cap 200, between the groove-like flow path 212 of the second shaft portion 70b and the first inner ring 402 of the first bearing 400, between the third shaft portion 70c and the inner ring stopper 460, and between the third shaft portion 70c and the sleeve 220. These flow spaces 216 form an in-rotor flow path 210.

[0074] The rotor passage 210 is a passage that extends along the axial direction of the rotating shaft 66 and may be, for example, a partially annular space in the axial direction. The rotor passage 210 extends from the first end to the second end of the permanent magnet 270 in the axial direction of the rotating shaft 66. The rotor passage 210 may be a groove or the like.

[0075] The rotor 62 is configured as described above. Next, the stator 64 will be described with reference to Figures 2 and 3. The stator 64, together with the rotor 62, constitutes the rotating electric machine 60. The stator 64 has a stator core 300 and a plurality of electromagnetic coils 310.

[0076] The stator core 300 is a cylindrical member. The stator core 300 is formed, for example, by laminating a plurality of ring-shaped electromagnetic steel plates in the axial direction. A plurality of slots are formed in the stator core 300. Teeth are located between adjacent slots.

[0077] The plurality of electromagnetic coils 310 includes a U-phase coil, a V-phase coil, and a W-phase coil. As can be understood from this, when the rotating electric machine 60 is a generator, the rotating electric machine 60 is a so-called three-phase power supply. Each of the plurality of electromagnetic coils 310 is configured by winding a conducting wire around the teeth portion of the stator core 300.

[0078] Of the multiple electromagnetic coils 310, the portions that protrude in the axial direction from the stator core 300 are the ends of the electromagnetic coils 310. The ends of the multiple electromagnetic coils 310 form coil end portions 314 shown in FIG.

[0079] For each of the multiple electromagnetic coils 310, the other end (terminal end 316) of the conductor that constitutes the electromagnetic coil 310 is drawn out from the coil end portion 314. The terminal ends 316 are bundled and connected to form a neutral point 318. The neutral point 318 is fixed to the coil end portion 314 by being inserted into a neutral point terminal 320.

[0080] The following is a brief description of the external configuration of the rotating electrical machine housing 22. As shown in Fig. 1, a first casing 40 and a second casing 42 are integrally provided on the outer peripheral surface near the left end of the main housing 24. In other words, the first casing 40 and the second casing 42 are parts of the main housing 24.

[0081] As shown in Fig. 2, a lower contact chamber 44 and an upper terminal chamber 46 are formed inside the first casing 40. The contact chamber 44 and the terminal chamber 46 are spaces independent of each other. The contact chamber 44 communicates with the stator chamber 36. The contact chamber 44 has a socket 48 formed therein that opens at a first end surface of the first casing 40. The socket 48 is closed by a cover member 45.

[0082] A U-phase terminal 110a, a V-phase terminal 110b, and a W-phase terminal 110c are housed in the terminal chamber 46. The U-phase terminal 110a, the V-phase terminal 110b, and the W-phase terminal 110c are electrically connected to the U-phase coil, the V-phase coil, and the W-phase coil of the electromagnetic coil 310, respectively, in the contact chamber 44. FIG. 2 illustrates a state in which the terminal portion 112 of the V-phase terminal 110b and the terminal wire 322 of the V-phase coil are connected via a screw 280.

[0083] 1, the second casing 42 is adjacent to the first casing 40. A thermistor 120, which is a temperature measuring device, is housed in the second casing 42. A harness 122 connected to the thermistor 120 is drawn out from the second casing 42 to the outside.

[0084] The rotating electrical machine system 20 configured as described above is provided with an air-cooling passage 730 (see FIG. 2) including the gas refrigerant passage 700, a first oil-cooling passage 800 (see FIG. 2), a lubricating oil passage 840 (see FIG. 3), and a second oil-cooling passage 870 (see FIG. 3). First, the air-cooling passage 730 will be described.

[0085] 2, the air-cooling flow path 730 includes an air supply path 732, a gas refrigerant flow path 700, a first branch path 734, a first drain path 736, a second branch path 738, and a second drain path 740. An air supply port serving as an entrance to the air supply path 732 is provided on the side circumferential surface of the first sub-housing 26. The first branch path 734 and the second branch path 738 are part of the rotor chamber 34. The second drain path 740 serves as both an oil discharge path and a gas refrigerant discharge path.

[0086] As shown in Fig. 2, the air supply passage 732 is formed inside the first sub-housing 26. The air supply passage 732 extends from the side peripheral surface of the first sub-housing 26 toward the inside of the first sub-housing 26. Note that although Fig. 2 shows an example of a configuration in which one air supply passage 732 is formed, multiple air supply passages 732 may be formed.

[0087] As described above, the gas refrigerant flow path 700 is a space formed between the second end surface of the first sub-housing 26 and the second wall surface 614 of the partition member 610. The gas refrigerant flow path 700 slopes from the first end to the second end as it approaches the inside of the first sub-housing 26.

[0088] The opening at the first end of the partition wall member 32 is an inlet into the rotor chamber 34 for the compressed air AR flowing out from the gas refrigerant flow path 700. The opening at the second end of the partition wall member 32 is an outlet from the rotor chamber 34 for the compressed air AR.

[0089] The first branch path 734 and the second branch path 738 branch off from each other at the magnetic stopper 272 within the rotor chamber 34. The first branch path 734 is a flow path that runs from the magnetic stopper 272 to the first bearing 400. The second branch path 738 is a flow path that runs through a clearance that extends along the axial direction between the magnetic stopper 272 and the partition member 32 and runs to the second bearing 500. Hereinafter, the portion of the compressed air AR that flows through the first branch path 734 will be referred to as "first branch air AR1," and the remaining portion that flows through the second branch path 738 will be referred to as "second branch air AR2."

[0090] 2 and 4 , the first branch path 734 includes a space formed between a first end surface of the magnet stopper 272 and a second end surface of the guide member 560, and a clearance formed between the inner ring stopper 460 and the guide member 560. As can be understood from this, the first proximal end 414 of the first bearing chamber 410 is included in the first branch path 734.

[0091] The first drain path 736 has a first conduit 742, a hollow portion 464, a second conduit 744, and a junction path 746. The inlet to the first conduit 742 is formed in the first sub-housing 26 at a location facing the communication hole 426 of the first bearing holder 420. The number of first drain paths 736 is not particularly limited, but is typically one to three. The outlet of the first conduit 742 communicates with the hollow portion 464.

[0092] The hollow portion 464 is a space that is surrounded by the annular wall portion 462 of the first sub-housing 26 and is closed by the resolver holder 56. The second guide path 744 is formed in the lower part of the first sub-housing 26 and extends linearly downward. The inlet of the second guide path 744 opens toward the hollow portion 464.

[0093] The junction channel 746 extends along the axial direction and is perpendicular to the second guide channel 744. The inlet of the junction channel 746 opens toward the second guide channel 744.

[0094] The second branch passage 738 is formed mainly between the outer peripheral surface of the permanent magnet 270 and the inner peripheral surface of the partition member 32. The opening at the second end of the partition member 32 is an outlet for the compressed air AR from the rotor chamber 34.

[0095] The main housing 24 has an air distribution passage 702 (shown in FIG. 2 ) therein. The inlet to the air distribution passage 702 faces the opening at the second end of the partition member 32. Therefore, a portion of the second diverted air AR2 flows into the air distribution passage 702. Hereinafter, the compressed air AR that flows into the air distribution passage 702 will be referred to as "diverted air Sb." The air distribution passage 702 communicates with an internal passage between the inner surface that forms the hollow recess 512 of the second sub-housing 28 and the outer surface of the straightening member 550. The outlet of the internal passage communicates with the second proximal end 524 of the second bearing chamber 520. The outlet of the internal passage also communicates with an air vent 554. The air vent 554 is an annular space formed between the second sub-housing 28 and the outer shaft 70.

[0096] The second branch passage 738 further includes a clearance between the outer peripheral surface of the collar 240 and the inner peripheral surface of the partition member 32, and the second distal end 522 of the second bearing chamber 520. The remainder of the second diverted air AR2 that does not flow into the air distribution passage 702 flows between the second bearing holder 530 and the inner inner ring stopper 540 at the second distal end 522 of the second bearing chamber 520. For ease of explanation, the remainder of the second diverted air AR2 flowing through the second branch passage 738 will hereinafter be referred to as the "main flow air Ms."

[0097] The second drain path 740 extends downward inside the main housing 24. A merged path 746 is orthogonally connected to the second drain path 740. In other words, the merged path 746 merges with the second drain path 740. The second drain path 740 extends to the outer surface of the rotating electrical machine housing 22.

[0098] As shown in Fig. 7, the compressed air AR discharged from the second drain path 740 is recovered in the gas-liquid separation device 900. As will be described later, the gas-liquid separation device 900 separates the compressed air AR from the cooling oil CO2 and the lubricating oil LO. The compressed air AR from which the oil has been separated is discharged from the gas-liquid separation device 900 to the atmosphere. The gas-liquid separation device 900 is an oil recovery device 901, and together with a circulation pump 902, which will be described later, constitutes an oil supply device 904. In this way, the gas-liquid separation device 900 serves as both the oil recovery device 901 and a part of the oil supply device 904.

[0099] The first oil cooling passage 800 will be described. The first oil cooling passage 800 is a passage for circulating and supplying cooling oil CO1 into the stator chamber 36. The first oil cooling passage 800 includes a first oil supply passage 802 connected to a tank 906, the stator chamber 36, and a stator chamber-side drain passage 804 connected to the tank 906. The first oil supply passage 802 is provided near the second end of the main housing 24. The stator chamber-side drain passage 804 is provided on the side of the first casing 40. The first oil supply passage 802 communicates with the stator chamber 36, and the stator chamber 36 communicates with the contact chamber 44 of the first casing 40 (see FIG. 2). The contact chamber 44 communicates with the stator chamber-side drain passage 804.

[0100] A first return pipe 910 is connected to the tank 906 to resupply the cooling oil CO1 to the first oil supply path 802. As shown in Fig. 7, the cooling oil CO1 that has circulated through the stator chamber side drain path 804 may be sent to the gas-liquid separator 900, and then sent from the gas-liquid separator 900 to the tank 906.

[0101] The lubricant oil flow path 840 will now be described. The lubricant oil flow path 840 is a flow path for circulating and supplying the lubricant oil LO to the first bearing 400 and the second bearing 500. The lubricant oil flow path 840 includes a second oil supply path 842, a first oil distribution path 846, a second oil distribution path 848, a first drain path 736, a third oil supply path 843, a third oil distribution path 852, and a second drain path 740.

[0102] The second oil supply passage 842 is formed in the upper part of the first sub-housing 26. The second oil supply passage 842 branches into a first oil distribution passage 846 and a second oil distribution passage 848 inside the first sub-housing 26. The first oil distribution passage 846 extends from the outer side in the radial direction of the first sub-housing 26 to the inner side in the radial direction. A communication hole 452 of the holder spacer 450 is located downstream of the first oil distribution passage 846. A first oil supply hole 424 of the first bearing holder 420 is located downstream of the communication hole 452.

[0103] The second oil distribution passage 848 branches off from the first oil distribution passage 846. The second oil distribution passage 848 is formed inside the first nozzle member 844 (see FIG. 3). An outlet portion 850 of the first nozzle member 844 faces the first distal end 412 of the first bearing chamber 410.

[0104] A first drain passage 736 including a hollow portion 464 is formed in the lower portion of the first sub-housing 26. The lubricating oil LO supplied to the first bearing 400 passes through the first drain passage 736 and then flows out of the rotating electrical machine housing 22 via the second drain passage 740. The lubricating oil LO discharged from the second drain passage 740 is collected in the gas-liquid separator 900.

[0105] The third oil distribution passage 852 is bent radially inward at the second end of the main housing 24. The third oil distribution passage 852 is connected to the second oil supply hole 536 formed in the second bearing holder 530. The third oil supply passage 843 joins with the third oil distribution passage 852 upstream of the second oil supply hole 536.

[0106] A second drain passage 740 communicating with the second bearing chamber 520 is formed in the lower part of the first sub-housing 26. The lubricating oil LO supplied to the second bearing 500 flows out of the rotating electrical machine housing 22 through the second drain passage 740. The lubricating oil LO discharged from the second drain passage 740 is collected in the gas-liquid separator 900.

[0107] The second oil cooling passage 870 is a passage for circulating and supplying cooling oil CO2 to the intra-rotor passage 210. The second oil cooling passage 870 includes a fourth oil supply passage 872 connected to the gas-liquid separator 900 via a third return pipe 914, the intra-rotor passage 210, and a second drain passage 740 connected to the tank 906. The fourth oil supply passage 872 is provided in the lower part of the first sub-housing 26. An oil guide passage 876 formed in the second nozzle member 874 is connected to the fourth oil supply passage 872. A discharge portion 878, which is an outlet of the oil guide passage 876, faces the first shaft portion 70a.

[0108] The screw cap 200 has an annular flow space 216. The flow space 216 is in communication with a groove-like flow passage 212 formed on the outer surface of the second shaft portion 70b and covered by the first inner ring 402 of the first bearing 400. The groove-like flow passage 212 further communicates with a second distal end 522 of the second bearing chamber 520 via a guide passage 214, the flow space 216 between the outer shaft 70 and the inner ring stopper 460, the flow space 216 between the outer shaft 70 and the magnetic stopper 272, the flow space 216 between the outer shaft 70 and the sleeve 220, and the internal space 242 between the outer shaft 70 and the collar 240.

[0109] The second bearing chamber 520 communicates with the second drain passage 740. The cooling oil CO2 that has flowed through the second drain passage 740 is discharged to the outside of the rotating electrical machine housing 22, similar to the lubricating oil LO. The cooling oil CO2 discharged from the second drain passage 740 is recovered in the gas-liquid separator 900. The cooling oil CO2 discharged from the gas-liquid separator 900 passes through the tank 906 and is returned to the fourth oil supply passage 872 via the third return pipe 914.

[0110] 7 is connected to an oil supply line 908 provided with a tank 906 and a circulation pump 902. The oil stored in the tank 906 is sent by the circulation pump 902 to a first return pipe 910, a second return pipe 912, and a third return pipe 914 connected to the circulation pump 902.

[0111] A recovery path (not shown) is connected to the gas-liquid separation device 900. The compressed air AR, cooling oil CO1, cooling oil CO2, and lubricating oil LO discharged from the second drain path 740 flow into the gas-liquid separation device 900 via the recovery path. As described above, the gas-liquid separation device 900 separates the compressed air AR from the oil. The compressed air AR is released into the atmosphere via the exhaust line 920. Meanwhile, the oil is temporarily stored in the tank 906. Thereafter, the lubricating oil LO is sucked from the tank 906 by the circulation pump 902 and sent to the first return pipe 910, the second return pipe 912, and the third return pipe 914. By repeating the above process, the oil in the tank 906 is circulated and supplied as the lubricating oil LO, the cooling oil CO1, or the cooling oil CO2.

[0112] It is also possible to use the lubricating oil LO and the cooling oil CO2 circulating through the rotor internal flow path 210. In this case, for example, the lubricating oil LO supplied to the second oil supply path 842 is distributed to the first nozzle member 844 and the second nozzle member 874.

[0113] The rotating electrical machine system 20 is basically configured as described above. Next, the gas turbine engine 950 will be described. The configuration of the gas turbine engine 950 is similar to the configuration shown in Fig. 8 of Japanese Patent Application Laid-Open No. 2022-157789, for example. Therefore, the description of the gas turbine engine 950 will be limited to an outline.

[0114] The gas turbine engine 950 includes an engine housing 952. The engine housing 952 includes an inner housing 954 and an outer housing 956. The inner housing 954 is connected to the second sub-housing 28 of the rotating electric machine system 20. The outer housing 956 is connected to the inner housing 954.

[0115] The inner housing 954 has a plurality of legs 958. In the illustrated example, the number of legs 958 is six. However, the number of legs 958 is determined depending on the connection strength required between the gas turbine engine 950 and the rotating electric machine system 20. In other words, the number of legs 958 is not limited to six as in the illustrated example. An intake space 960 is formed between the plurality of legs 958.

[0116] The gas turbine engine 950 includes an output shaft 964 connected to the rotary shaft 66. A compressor wheel (not shown) and a turbine wheel (not shown) are mounted on the outer diametrical side of the output shaft 964. The compressor wheel and the turbine wheel are rotatable integrally with the rotary shaft 66 and the output shaft 964.

[0117] The operation of the combined power system 10 will now be described.

[0118] First, an alternating current is supplied to a plurality of electromagnetic coils 310 (U-phase coil, V-phase coil, and W-phase coil) via U-phase terminal 110a, V-phase terminal 110b, and W-phase terminal 110c. When the alternating current flows through the electromagnetic coils 310, an alternating magnetic field is generated in the stator 64. As a result, attractive and repulsive forces act alternately between the electromagnetic coils 310 and the permanent magnets 270 of the rotor 62. As a result, the rotating shaft 66 begins to rotate. Alternatively, the rotating shaft 66 may be rotated by a known starter (not shown).

[0119] When the rotary shaft 66 starts to rotate, the output shaft 964 also starts to rotate integrally with the rotary shaft 66. Accordingly, the compressor wheel and the turbine wheel supported by the output shaft 964 rotate integrally with the output shaft 964.

[0120] After the gas turbine engine 950 is started in the above manner, the output shaft 964 rotates in accordance with the operation of the gas turbine engine 950. Therefore, even if the supply of current to the electromagnetic coil 310 is stopped, the rotary shaft 66 rotates integrally with the output shaft 964.

[0121] Because the rotating shaft 66 holds the permanent magnet 270, an AC current is generated in the electromagnetic coil 310 surrounding the permanent magnet 270. The AC current is sent to a current converter (not shown) via the U-phase terminal 110a, the V-phase terminal 110b, and the W-phase terminal 110c. The current converter converts the AC current to a DC current. When a control circuit (not shown) determines that the output of an external load electrically connected to the battery has decreased, the current converter supplies a DC current to the battery. This charges the battery.

[0122] As the output shaft 964 rotates, air is drawn into the engine housing 952 through an intake space 960 between the legs 958 of the inner housing 954. The second sub-housing 28 of the rotating electric machine system 20 has a mountain-like shape that narrows in diameter from the main housing 24 toward the engine housing 952. Therefore, the drawn air is rectified by the second sub-housing 28 so that it flows toward the engine housing 952. Because the second end of the second sub-housing 28 is inserted into the opening at the first end of the engine housing 952, the air is efficiently guided into the engine housing 952.

[0123] The atmospheric air drawn into the engine housing 952 is compressed by the compressor wheel, thereby generating compressed air AR. A portion of this compressed air AR is bled and supplied to an air intake port provided on the outer peripheral surface of the first sub-housing 26. Note that the compressed air AR obtained by compressing the atmospheric air with a compressor may also be supplied to the air intake port. Alternatively, compressed gas may be supplied to the air intake port from an oxygen cylinder, nitrogen cylinder, or the like.

[0124] The compressed air AR that flows into the air supply passage 732 through the air supply port flows into the gas refrigerant flow path 700 formed between the second end surface of the first sub-housing 26 and the second wall surface 614 of the partition member 610. The compressed air AR moves through the gas refrigerant flow path 700 toward the rotor chamber 34 inside the rotating electrical machine housing 22.

[0125] The compressed air AR flows from the gas refrigerant flow path 700 into the rotor chamber 34 through the opening at the first end of the partition member 32. In the rotor chamber 34, the compressed air AR is divided into first diverted air AR1 and second diverted air AR2, with the magnetic stopper 272 as the boundary. The first diverted air AR1 travels along the first branch path 734 to reach the first proximal end 414 of the first bearing chamber 410, and forms an air curtain at the first proximal end 414. The first bearing 400 is cooled by the air curtain.

[0126] As shown in FIG. 4 , the excess first diverged air AR1 passes through the relay hole 446 of the spacer ring 440 and the communication hole 426 of the first bearing holder 420, and flows into the first drain path 736. As described above, the first drain path 736 has the first conduit 742, the hollow portion 464, the second conduit 744, and the merging path 746. The first diverged air AR1 that passes through the communication hole 426 first flows into the first conduit 742 formed in the first sub-housing 26. Because the first conduit 742 communicates with the second conduit 744 via the hollow portion 464, and the second conduit 744 communicates with the merging path 746, the first diverged air AR1 flows sequentially through the hollow portion 464, the second conduit 744, and the merging path 746. Thereafter, the first diverted air flow AR1 flows from the junction flow path 746 into the second drain path 740.

[0127] As shown in FIG. 5 , the second diverged air AR2 flows inside the rotor chamber 34, which is part of the second branch path 738. Inside the rotor chamber 34, the second diverged air AR2 flows mainly between the outer peripheral surfaces of the permanent magnets 270 and the inner peripheral surface of the partition member 32. At this time, the second diverged air AR2 comes into contact with the permanent magnets 270. This contact cools the rotor 62. After cooling the rotor 62, the second diverged air AR2 is separated at the opening at the second end of the partition member 32 into mainstream air Ms, which flows through the second branch path 738, and branch air Sb, which flows through the air distribution path 702.

[0128] The mainstream air Ms reaches the second distal end 522 of the second bearing chamber 520. Meanwhile, the branch air Sb passes between the inner surface that forms the hollow recess 512 of the second sub-housing 28 and the outer surface of the rectifying member 550, and reaches the second proximal end 524 of the second bearing chamber 520. The excess branch air Sb is discharged to the outside of the rotating electric machine housing 22 through an air vent 554 formed between the second sub-housing 28 and the outer shaft 70. By discharging the excess compressed air AR to the outside of the rotating electric machine housing 22 in this way, the pressure of the compressed air AR flowing inside the rotating electric machine housing 22 is adjusted to be approximately constant.

[0129] As can be understood from the above, an air curtain is formed in the second bearing chamber 520 to surround the second bearing 500. The second bearing 500 is cooled by the air curtain.

[0130] The second diverted air AR2 supplied to the second bearing chamber 520 is guided by the inner surface 551 of the straightening member 550 and flows toward the second drain path 740. In the second drain path 740, the first diverted air AR1 and the second diverted air AR2 merge. Here, the lubricating oil LO is supplied to the first bearing 400 and the second bearing 500, respectively. Therefore, the first diverted air AR1 that has passed through the first bearing chamber 410 is a gas-liquid mixture. Similarly, the second diverted air AR2 that has passed through the second bearing chamber 520 is also a gas-liquid mixture. The first diverted air AR1 and the second diverted air AR2 that have passed through the merging path 746 flow from the rotating electrical machine housing 22 toward the gas-liquid separation device 900.

[0131] The compressed air AR and oil (for example, lubricating oil LO) are separated in the gas-liquid separator 900. The compressed air AR from which the oil has been separated is discharged from the gas-liquid separator 900 to the atmosphere.

[0132] As described above, the compressed air AR flows through the rotary electric machine housing 22, and at the same time, the cooling oil CO1, the cooling oil CO2, and the lubricating oil LO flow through the rotary electric machine housing 22. The flow paths of the cooling oil CO1, the cooling oil CO2, and the lubricating oil LO will be described.

[0133] In the first oil cooling flow path 800, cooling oil CO1 is supplied from the tank 906 to the first oil supply path 802. Because the first oil supply path 802 is connected to the stator chamber 36, the cooling oil CO1 moves toward the stator chamber-side drain path 804 while filling the stator chamber 36. In this way, the stator 64 in the stator chamber 36 is immersed in the cooling oil CO1. This cools the stator 64.

[0134] As the cooling oil CO1 in the stator chamber 36 flows toward the stator chamber-side drain path 804, the cooling oil CO1 cools the neutral point 318 and the neutral point terminal 320. In addition, heat transfer from the coil end portion 314 to the neutral point terminal 320 is reduced.

[0135] The cooling oil CO1 in the stator chamber 36 flows toward the first casing 40 along the first wall surface 612 of the partition member 610. As can be seen from this, the flow direction of the cooling oil CO1 flowing along the first wall surface 612 of the partition member 610 and the flow direction of the compressed air AR flowing along the second wall surface 614 of the partition member 610 are opposite to each other.

[0136] The cooling oil CO1 that has circulated through the stator chamber 36 flows from a first end of the stator chamber 36 into the contact chamber 44 of the first casing 40. The cooling oil CO1 in the contact chamber 44 comes into contact with the terminal portion 112, the terminal wire 322, and the screw 280. This cools the electrical contact between the U-phase terminal 110a and the U-phase coil. For the same reason, the electrical contact between the V-phase terminal 110b and the V-phase coil is also cooled. The electrical contact between the W-phase terminal 110c and the W-phase coil is also cooled.

[0137] The cooling oil CO1 in the contact chamber 44 is collected in the tank 906 via the stator chamber side drain path 804. Thereafter, the cooling oil CO1 is resupplied from the tank 906 to the first oil supply path 802 via the first return pipe 910. Note that the cooling oil CO1 that has circulated through the stator chamber side drain path 804 may be sent to the gas-liquid separator 900, and then sent from the gas-liquid separator 900 to the tank 906.

[0138] In the lubricant oil flow path 840, the lubricant oil LO is supplied from the tank 906 to the second oil supply passage 842. A portion of the lubricant oil LO is supplied to the first outer ring 406 of the first bearing 400 via the first oil distribution passage 846, the communication hole 452 of the holder spacer 450, and the first oil supply hole 424 of the spacer ring 440. Another portion of the lubricant oil LO flows from the first oil distribution passage 846 into the second oil distribution passage 848 formed in the first nozzle member 844 and is further discharged from a discharge portion 850 provided in the first nozzle member 844 to the first distal end 412 of the first bearing chamber 410. Therefore, the supply direction of the lubricant oil LO to the first bearing chamber 410 is a first direction from the first bearing chamber 410 toward the permanent magnet 270. The lubricant oil LO supplied to the first bearing 400 in this manner cools and lubricates the first bearing 400. Thereafter, the lubricating oil LO passes through the hollow portion 464 of the first sub-housing 26 and the first drain passage 736 and is collected in the gas-liquid separator 900.

[0139] Another portion of the lubricating oil LO flows from the second oil supply passage 842 into the third oil distribution passage 852 and is supplied to the second outer ring 506 of the second bearing 500 via the second oil supply hole 536 formed in the second bearing holder 530. The lubricating oil LO is also supplied to the second bearing 500 from a discharge port 556 provided in the main housing 24. This lubricating oil LO cools and lubricates the second bearing 500. The lubricating oil LO is then collected in the gas-liquid separator 900 via the second drain passage 740 communicating with the second bearing chamber 520.

[0140] As described above, the first diverted air AR1 supplied to the first proximal end 414 of the first bearing chamber 410 forms an air curtain. It is difficult for the lubricating oil LO supplied to the first bearing 400 to pass through the air curtain and infiltrate into the rotor chamber 34. In the second bearing chamber 520, the mainstream air Ms supplied to the second distal end 522 and the diverted air Sb supplied to the second proximal end 524 form an air curtain. It is difficult for the lubricating oil LO supplied to the second bearing 500 to pass through the air curtain and infiltrate into the rotor chamber 34. This prevents the lubricating oil LO from infiltrating into the rotor chamber 34. This particularly prevents the permanent magnets 270 from being contaminated with the lubricating oil LO.

[0141] It is also difficult for the lubricating oil LO to seep from the second bearing chamber 520 into the hollow recess 512 of the second sub-housing 28. Therefore, it is possible to prevent the rectifying member 550 from being contaminated with the lubricating oil LO.

[0142] The lubricating oil LO contains compressed air AR that has formed an air curtain. The gas-liquid separator 900 separates this compressed air AR from the lubricating oil LO. The lubricating oil LO from which the compressed air AR has been separated is temporarily stored in a tank 906, and then re-supplied from the second return pipe 912 to the second oil supply passage 842.

[0143] The cooling oil CO2 flowing through the rotor internal flow path 210 will be described.

[0144] In the second oil cooling flow path 870, cooling oil CO2 is supplied from the tank 906 to the fourth oil supply path 872 and flows through an oil guide path 876 formed in the second nozzle member 874. The cooling oil CO2 is discharged from a discharge port 878 provided in the second nozzle member 874 toward the first shaft portion 70a of the outer shaft 70. The cooling oil CO2 flows through the rotor inner flow path 210 from the first end to the second end along the axial direction of the rotating shaft 66. Specifically, the cooling oil CO2 passes through a flow space 216 between the screw cap 200 and the first shaft portion 70a, a groove-shaped flow path 212 covered by the first inner ring 402 of the first bearing 400, a guide flow path 214, a flow space 216 between the outer shaft 70 and the inner ring stopper 460, a flow space 216 between the outer shaft 70 and the magnet stopper 272, and a flow space 216 between the outer shaft 70 and the sleeve 220.

[0145] The cooling oil CO2 that reaches the flow space 216 between the outer shaft 70 and the sleeve 220 flows into the communicating flow passage 232 through the inlet 234 at the second end of the sleeve 220. The communicating flow passage 232 is inclined from the inner side to the outer side in the diameter direction of the rotating shaft 66 as it moves from the upstream side to the downstream side in the flow direction of the cooling oil CO2. Centrifugal force acts on the rotating shaft 66. This centrifugal force causes the cooling oil CO2 to easily move along the communicating flow passage 232 toward the first inner chamber 242a.

[0146] The cooling oil CO2 that has flowed through the communicating flow passage 232 flows into the first inner chamber 242a, which is part of the internal space 242. An inner circumferential surface 256a that forms the first inner chamber 242a in the collar 240 abuts against the abutment surface 230 of the first annular protrusion 226. An outlet 236 for the cooling oil CO2 to the communicating flow passage 232 is located inward of the abutment surface 230 in the radial direction of the rotating shaft 66. In other words, the abutment surface 230 does not have an outlet 236 (such as a notch or hole). Therefore, the entire abutment surface 230 abuts against the inner circumferential surface 256a of the first inner chamber 242a.

[0147] As the rotor 62 rotates, centrifugal force acts on the sleeve 220 and the collar 240. This centrifugal force causes the insertion portion 224 and the cylindrical portion 244 to deform so as to bulge slightly outward in the radial direction of the rotary shaft 66. As described above, the abutment surface 230 is not provided with an outlet 236. Based on this, even when the rotor 62 rotates at high speed, the surface pressure of the abutment surface 230 against the inner circumferential surface 256a of the first inner chamber 242a is maintained. This maintains a seal between the abutment surface 230 and the inner circumferential surface 256a. Therefore, leakage of the cooling oil CO2 from between the abutment surface 230 and the inner circumferential surface 256a is prevented.

[0148] For the reasons described above, the cooling oil CO2 can be easily moved from the first inner chamber 242a to the second inner chamber 242b via the discharge flow path 254. In other words, the cooling oil CO2 is prevented from being discharged from any location other than the opening at the second end of the second inner chamber 242b. The direction from the first inner chamber 242a to the second inner chamber 242b is a direction away from the sleeve 220 and the permanent magnet 270. In other words, with the above configuration, the cooling oil CO2 can be easily directed in a direction away from the permanent magnet 270. Therefore, even if the rotor 62 is an SPM type, the permanent magnet 270 is less likely to be contaminated with the cooling oil CO2.

[0149] The cooling oil CO2 is discharged to the outside of the second internal chamber 242b from the opening at the second end of the collar 240. After circulating through the rotor internal flow path 210 and the internal space 242 in the above manner, the cooling oil CO2 reaches the second distal end 522 of the second bearing chamber 520.

[0150] At the second distal end 522, the cooling oil CO2 mixes with the compressed air AR. The cooling oil CO2 containing the compressed air AR merges with the lubricating oil LO in the second drain path 740. Thereafter, the cooling oil CO2, like the lubricating oil LO, is recovered in the gas-liquid separator 900 via the second drain path 740. The cooling oil CO2 from which the compressed air AR has been separated in the gas-liquid separator 900 is temporarily stored in the tank 906 and then returned to the fourth oil supply path 872 via the third return pipe 914.

[0151] As described above, in this embodiment, the same oil is used as the lubricating oil LO (lubricant) and the cooling oil CO1 and cooling oil CO2 (both liquid refrigerants). Therefore, it is possible to combine the circulation supply flow path for the lubricant and the circulation supply flow path for the liquid refrigerant. This simplifies the configuration of the circulation supply flow path for the lubricant and the circulation supply flow path for the liquid refrigerant. However, the lubricant and the liquid refrigerant may be different liquids.

[0152] The effects of this embodiment can be summarized as follows.

[0153] The sleeve 220 has an insertion portion 224 at one end (second end) in the axial direction of the sleeve 220. The insertion portion 224 is inserted into the internal space 242 of the collar 240, and separates the internal rotor flow path 210 from the internal space 242. The sleeve 220 further has a communication flow path 232 formed in the insertion portion 224, which communicates between the internal rotor flow path 210 and the internal space 242. All or part of the outer circumferential surface of the insertion portion 224 is an abutment surface 230 with which an inner circumferential surface 256a of the first internal chamber 242a of the collar 240 abuts.

[0154] The sleeve 220 further has an inlet 234 through which the cooling oil CO2, which is a liquid refrigerant, flows from the rotor internal flow path 210 into the communicating flow path 232, and an outlet 236 through which the cooling oil CO2 flows from the communicating flow path 232 to the internal space 242 (first internal chamber 242a). In the radial direction of the rotating shaft 66, the outlet 236 is located inward from the contact surface 230.

[0155] According to this configuration, it is not necessary to form the outlet 236 in the abutment surface 230. Therefore, it is not necessary to cut out a portion of the abutment surface 230 along the axial direction in order to form the outlet 236 in the abutment surface 230. Therefore, the entire abutment surface 230 abuts against the inner circumferential surface 256a of the first internal chamber 242a of the collar 240.

[0156] As the rotor 62 rotates, centrifugal force acts on the sleeve 220 and the collar 240. This centrifugal force causes the insertion portion 224 and the cylindrical portion 244 to deform, slightly bulging outward in the radial direction of the rotary shaft 66. Because the abutment surface 230 does not have an outlet 236, the surface pressure of the abutment surface 230 against the inner circumferential surface 256a of the first internal chamber 242a is maintained during rotation of the rotor 62. This maintains a seal between the abutment surface 230 and the inner circumferential surface 256a. This prevents the cooling oil CO2 from leaking from between the abutment surface 230 and the inner circumferential surface 256a. As a result, the cooling oil CO2 is prevented from being discharged from any location other than the opening at the second end of the second internal chamber 242b.

[0157] As the communication flow path 232 approaches the internal space 242 from the internal rotor flow path 210, it inclines from the inside to the outside in the diameter direction of the rotary shaft 66. The direction from the internal rotor flow path 210 toward the internal space 242 is the direction from upstream to downstream in the flow direction of the cooling oil CO2.

[0158] When the rotary shaft 66 rotates, centrifugal force acts on the rotary shaft 66. This centrifugal force causes the cooling oil CO2 to easily move along the communicating flow passage 232 toward the internal space 242 (first internal chamber 242a). In other words, with this configuration, the flow of the cooling oil CO2 within the communicating flow passage 232 is assisted.

[0159] The collar 240 has a partition wall 246 that divides the internal space 242 into a first internal chamber 242a and a second internal chamber 242b. An insertion hole 248 and a discharge flow path 254 are formed in the partition wall 246. The discharge flow path 254 connects the first internal chamber 242a and the second internal chamber 242b. The insertion portion 224 is inserted into the first internal chamber 242a, and the liquid refrigerant supplied to the in-rotor flow path 210 flows from the first internal chamber 242a through the discharge flow path 254 and is discharged from the second internal chamber 242b to the outside of the collar 240.

[0160] By inserting the rotary shaft 66 into the insertion hole 248, it is easy to hold the collar 240 on the rotary shaft 66. In addition, the cooling oil CO2 that has circulated through the rotor internal flow path 210 can be quickly discharged in a direction away from the contact surface 230 via the communication flow path 232, the internal space 242, and the discharge flow path 254.

[0161] The insertion portion 224 has a first annular protrusion 226 that protrudes annularly in the axial direction from a second end of the main body portion 225 of the sleeve 220, and a second annular protrusion 228 that protrudes annularly in the axial direction from the second end of the first annular protrusion 226. The outer diameter of the second annular protrusion 228 is smaller than the outer diameter of the first annular protrusion 226. In other words, the second annular protrusion 228 has a smaller diameter than the first annular protrusion 226. The outer peripheral surface of the first annular protrusion 226 includes an abutment surface 230, and the second annular protrusion 228 has an outlet 236.

[0162] In the insertion portion 224, the distance (outer diameter) from the center of the diameter of the rotary shaft 66 to the abutment surface 230 can be made smaller than when the first annular protrusion 226 is not present. This allows the inner diameter of the collar 240 to be made smaller. This makes it possible to make the collar 240 thinner and lighter.

[0163] The liquid refrigerant supply device is an oil supply device 904 that supplies cooling oil CO1 and cooling oil CO2 as liquid refrigerants. The rotating electrical machine housing 22 has a lubricating oil flow path 840 for supplying lubricating oil LO from the oil supply device 904 to the first bearing 400 and the second bearing 500 that support the rotating shaft 66.

[0164] A portion of the lubricating oil LO for lubricating the first bearing 400 and the second bearing 500 can be supplied from the oil supply device 904 to the rotating electrical machine housing 22 via a system separate from the lubricating oil LO, and used as a liquid refrigerant (cooling oil CO1 and cooling oil CO2). Therefore, one oil supply device 904 can be used as a device that supplies both the lubricating oil LO and the cooling oil CO1 and cooling oil CO2. This reduces capital investment. Furthermore, the configuration of the rotating electrical machine system 20 can be simplified.

[0165] The rotating electrical machine housing 22 has an oil discharge path (second drain path 740) that discharges the cooling oil CO2 that has flowed through the intra-rotor flow path 210 and the lubricating oil LO that has flowed through the lubricating oil flow path 840 to the oil supply device 904. The oil supply device 904 resupplies the oil discharged from the oil discharge path to the intra-rotor flow path 210 and the lubricating oil flow path 840.

[0166] According to this configuration, the lubricating oil LO supplied to the first bearing 400 and the second bearing 500 and the cooling oil CO2 that has cooled the rotor 62 are discharged from the rotary electric machine housing 22, while new lubricating oil LO is supplied to the first bearing 400 and the second bearing 500 and new cooling oil CO2 is supplied to the rotor 62. Therefore, it is possible to continuously lubricate the first bearing 400 and the second bearing 500 and to continuously cool the rotor 62. Moreover, because the oil is circulated and supplied, costs are lower than when new oil is continuously supplied.

[0167] The rotating electric machine system 20 includes a gas refrigerant supply device that supplies a gas refrigerant to the first bearing 400 and the second bearing 500. In one aspect, the gas refrigerant supply device is a gas turbine engine 950 that, together with the rotating electric machine system 20, constitutes the combined power system 10. In another aspect, the gas refrigerant supply device is a compressor that compresses atmospheric air. In these cases, the gas refrigerant is compressed air AR. In still another aspect, the gas refrigerant supply device includes a container that stores compressed gas.

[0168] The rotating electrical machine housing 22 has a gas refrigerant flow path 700 through which the gas refrigerant flows, and a gas refrigerant discharge path (second drain path 740) for discharging the gas refrigerant to the outside of the rotating electrical machine housing 22. The oil supply device 904 recovers the gas refrigerant that has flowed through the gas refrigerant discharge path and the oil (lubricating oil LO and cooling oil CO2) that has flowed through the oil discharge path (second drain path 740), and supplies the recovered oil again to the rotor internal flow path 210 and the lubricating oil flow path 840.

[0169] Because the oil supply device 904 collects both the gas refrigerant and the oil, there is no need to collect the gas refrigerant and the oil separately. Therefore, there is no need to include a gas refrigerant collection device separate from the oil supply device 904 in the rotating electric machine system 20. This prevents the configuration of the rotating electric machine system 20 from becoming complicated.

[0170] The oil supply system 904 includes a gas-liquid separator 900 that separates the gas refrigerant from the oil.

[0171] Because the gas-liquid separator 900 separates the gaseous refrigerant from the oil, even though the gaseous refrigerant and the oil are recovered together, it is possible to resupply only the oil to the rotor internal flow path 210 and the lubricating oil flow path 840. That is, with this configuration, it is easy to circulate and supply the lubricating oil LO to the first bearing 400 and the second bearing 500.

[0172] The following additional notes are further disclosed regarding the above embodiment.

[0173] (Appendix 1) A rotating electric machine system (20) according to the present disclosure is a rotating electric machine system including a rotating electric machine (60) having a rotor (62) and a stator (64), and a housing (22) that houses the stator.

[0174] The rotor has a rotating shaft (66), a sleeve (220) that covers the rotating shaft from the outer circumferential side, a permanent magnet (270) held in the sleeve, a collar (240) that is arranged on the outer circumferential side of the sleeve and the rotating shaft, a rotor internal flow path (210) that is formed between the outer circumferential surface of the rotating shaft and the inner circumferential surface of the sleeve and includes an annular space that extends along the axial direction of the rotating shaft, and an internal space (242) that is formed between the outer circumferential surface of the rotating shaft and the inner circumferential surface (256) of the collar.

[0175] The rotating electrical machine system includes a liquid refrigerant supply device (904) that supplies a liquid refrigerant (CO2) to the internal rotor flow path. The sleeve has an insertion portion (224) at one end of the sleeve in the axial direction, which is inserted into the internal space and separates the internal rotor flow path from the internal space, and a communication flow path (232) formed in the insertion portion that communicates the internal rotor flow path with the internal space. The outer peripheral surface of the insertion portion includes an abutment surface (230) that abuts against the inner peripheral surface of the collar.

[0176] In the above configuration, the outlet (236) through which the liquid refrigerant flows from the communication channel into the internal space is located inward of the contact surface in the diameter direction of the rotary shaft.

[0177] This configuration eliminates the need to form an inlet and an outlet by cutting out a portion of the abutment surface of the sleeve, thereby preventing liquid refrigerant from leaking between the abutment surface of the sleeve and the inner circumferential surface of the collar.

[0178] (Appendix 2) In the rotating electrical machine system described in Supplementary Note 1, the communication passage may be inclined from the inside to the outside in the diameter direction as it approaches the internal space from the rotor passage.

[0179] When the rotating shaft rotates, centrifugal force acts on the liquid refrigerant, so when the communicating passage is inclined as described above, the liquid refrigerant easily moves through the communicating passage from the rotor passage toward the internal space.

[0180] (Appendix 3) In the rotating electric machine system described in Supplementary Note 1 or 2, the collar may have a partition wall (246) that divides the internal space into a first inner chamber (242a) and a second inner chamber (242b), an insertion hole (248) formed in the partition wall and through which the rotating shaft is inserted, and a discharge flow path (254) formed in the partition wall that communicates the first inner chamber and the second inner chamber, and the insertion portion may be inserted into the first inner chamber, and the liquid refrigerant supplied to the rotor internal flow path may be discharged from the first inner chamber through the discharge flow path and from the second inner chamber to the outside of the collar.

[0181] With this configuration, the liquid refrigerant supplied to the rotor internal flow path can be quickly discharged in a direction away from the contact surface via the communication flow path, the internal space, and the discharge flow path.

[0182] (Appendix 4) In the rotating electric machine system described in any one of Appendices 1 to 3, the insertion portion may have a first annular convex portion (226) that protrudes in an annular shape along the axial direction of the sleeve, and a second annular convex portion (228) that is connected to the first annular convex portion, protrudes in an annular shape along the axial direction of the sleeve, and has a smaller diameter than the first annular convex portion, and the outer peripheral surface of the first annular convex portion may include the abutment surface, and the second annular convex portion may have the outlet.

[0183] In the insertion portion, the distance (outer diameter) from the center of the rotary shaft to the abutment surface can be made smaller than when the first annular convex portion is not present, which allows the inner diameter of the collar to be made smaller, thereby making it possible to make the collar thinner and lighter.

[0184] (Appendix 5) In the rotating electric machine system described in any one of Appendices 1 to 4, the liquid refrigerant supply device may be an oil supply device (904) that supplies oil as the liquid refrigerant, and the housing may have a lubricating oil flow path (840) for supplying the oil as a lubricant (LO) to bearings (400, 500) that support the rotating shaft.

[0185] In this case, part of the lubricating oil for lubricating the bearings can be used as the liquid refrigerant. Therefore, one device can be used as both an oil supply device and a liquid refrigerant supply device. This reduces capital investment and simplifies the configuration of the rotating electrical machine system.

[0186] (Appendix 6) In the rotating electric machine system described in Appendix 5, the housing has an oil discharge passage (740) that discharges the oil that has circulated through the rotor internal flow path and the lubricating oil flow path to the oil supply device, and the oil supply device may re-supply the oil discharged from the oil discharge passage to the rotor internal flow path and the lubricating oil flow path.

[0187] With this configuration, the oil supplied to the bearings (lubricating oil) and the oil used to cool the rotor (cooling oil) can be discharged from the housing while new oil is supplied to the bearings and rotor. This allows the bearings to be continuously lubricated and the rotor to be continuously cooled. Furthermore, because the oil is circulated and supplied, costs are lower than when new oil is continuously supplied.

[0188] (Appendix 7) The rotating electric machine system described in Appendix 6 may further include a gas refrigerant supply device (950) that supplies a gas refrigerant (AR) to the bearing, the housing having a gas refrigerant flow path (700) through which the gas refrigerant flows and a gas refrigerant discharge path (740) for discharging the gas refrigerant to the outside of the housing, and the oil supply device may recover the gas refrigerant that has flowed through the gas refrigerant discharge path and the oil that has flowed through the oil discharge path, and resupply the oil to the lubricating oil flow path.

[0189] Since the oil supply device collects both the gas refrigerant and the oil, there is no need to collect the gas refrigerant and the oil separately. Therefore, there is no need to provide a gas refrigerant collection device in the rotating electrical machine system. This avoids the configuration of the rotating electrical machine system becoming complicated.

[0190] (Appendix 8) In the rotating electrical machine system described in Supplementary Note 7, the oil supply device may include a gas-liquid separator (900) that separates the gas refrigerant and the oil.

[0191] The gas-liquid separator separates the gas refrigerant from the oil, so even though the gas refrigerant and oil are recovered together, it is possible to resupply only the oil to the oil supply passage. In other words, this configuration makes it easy to circulate lubricating oil to the bearings.

[0192] The present invention is not limited to the above disclosure, and various configurations can be adopted without departing from the gist of the present invention. [Explanation of symbols]

[0193] 10...Composite power system 20...Rotating electric system 22... Rotating electric machine housing 60... Rotating electric machine 62...Rotor 64...Stator 66...rotating shaft 210...flow path inside rotor 220...Sleeve 224...Insertion part 226...First annular convex portion 228...Second annular convex portion 230...Abutment surface 232...Communicating flow path 234…Entrance 236…Exit 240...Color 242...Interior space 242a...First inner chamber 242b...Second inner chamber 246...Demarcation wall 248...Through hole 254...Discharge flow path 256...Inner surface 270...Permanent magnet 310...Electromagnetic coil 400...1st bearing 500...2nd bearing 730...Air cooling passage 736...First drain passage 740...Second drain passage 800...First oil cooling passage 840...Lubricating oil flow path 870...Second oil cooling flow path 900…Gas-liquid separation device 904…Oil supply device 950...Gas turbine engine AR...Compressed air CO1, CO2…Cooling oil LO…Lubricating oil

Claims

1. A rotating electric machine system including a rotating electric machine having a rotor and a stator, and a housing that accommodates the stator, the rotor has a rotating shaft, a sleeve that covers the rotating shaft from an outer peripheral side, a permanent magnet held by the sleeve, a collar that is arranged on the outer peripheral side of the sleeve and the rotating shaft, a rotor internal flow path that includes an annular space that is formed between an outer peripheral surface of the rotating shaft and an inner peripheral surface of the sleeve and extends along the axial direction of the rotating shaft, and an internal space that is formed between the outer peripheral surface of the rotating shaft and the inner peripheral surface of the collar, the rotating electrical machine system includes a liquid refrigerant supply device that supplies a liquid refrigerant to the rotor internal flow path, the sleeve has an insertion portion that is one end of the sleeve in the axial direction and is inserted into the internal space to separate the internal rotor flow path from the internal space, and a communication flow path that is formed in the insertion portion and communicates the internal rotor flow path with the internal space, an outer peripheral surface of the insertion portion includes an abutment surface with which the inner peripheral surface of the collar abuts; an outlet for the liquid refrigerant to flow from the communication channel into the internal space is located inward of the contact surface in a diameter direction of the rotating shaft.

2. 2. The rotating electrical machine system according to claim 1, wherein the communication passage is inclined from the inside to the outside in the radial direction as it approaches the internal space from the rotor passage.

3. 2. The rotating electric machine system according to claim 1, wherein the collar has a partition wall that divides the internal space into a first inner chamber and a second inner chamber, an insertion hole formed in the partition wall and through which the rotating shaft is inserted, and a discharge flow path formed in the partition wall that communicates between the first inner chamber and the second inner chamber, the insertion portion is inserted into the first inner chamber, and the liquid refrigerant supplied to the rotor inner flow path is discharged from the first inner chamber through the discharge flow path and from the second inner chamber to the outside of the collar.

4. 2. The rotating electric machine system according to claim 1, wherein the insertion portion has a first annular convex portion that protrudes annularly along the axial direction of the sleeve, and a second annular convex portion that is connected to the first annular convex portion, protrudes annularly along the axial direction of the sleeve, and has a smaller diameter than the first annular convex portion; an outer peripheral surface of the first annular protrusion including the abutment surface, and the second annular protrusion having the outlet;

5. 5. The rotating electrical machine system according to claim 1, wherein the liquid refrigerant supply device is an oil supply device that supplies oil as the liquid refrigerant, The housing has a lubricating oil passage for supplying the oil as a lubricant to a bearing that supports the rotating shaft.

6. 6. A rotating electric machine system according to claim 5, wherein the housing has an oil discharge passage that discharges the oil that has circulated through the rotor internal flow path and the lubricating oil flow path to the oil supply device, and the oil supply device re-supplies the oil discharged from the oil discharge passage to the rotor internal flow path and the lubricating oil flow path.

7. 7. The rotating electrical machine system according to claim 6, further comprising a gas refrigerant supply device that supplies a gas refrigerant to the bearing, the housing has a gas refrigerant flow path through which the gas refrigerant flows and a gas refrigerant discharge path for discharging the gas refrigerant to the outside of the housing, The oil supply device recovers the gaseous refrigerant that has flowed through the gaseous refrigerant discharge passage and the oil that has flowed through the oil discharge passage, and resupplies the oil to the lubricating oil passage.

8. 8. The rotating electrical machine system according to claim 7, wherein the oil supply device includes a gas-liquid separator that separates the gas refrigerant from the oil.

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