Rotating Electrical Machine System

Abstract

To provide a rotating electric machine system that can efficiently recover lubricating oil. [Solution] The rotating electric machine housing 18 of the rotating electric machine system 12 is provided with a first bearing chamber 39 for housing a first bearing 38. Inside the first bearing chamber 39 is provided a first oil nozzle 138 having a first discharge port for discharging lubricating oil LO toward the first bearing 38, and an oil splash prevention cover 170 that covers the first bearing 38 so as to face the first bearing 38 in the axial direction. The first discharge port is located inside the oil splash prevention cover 170.

Description

Technical Field

[0001] The present disclosure relates to a rotating electrical machine system.

Background Art

[0002] Japanese Patent Application Laid-Open No. 2024-25367 discloses a rotating electrical machine system including a rotor and a stator. A bearing for rotatably supporting the rotor is arranged in the rotating electrical machine system. Lubricating oil is supplied to the bearing.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] When lubricating oil is discharged toward the bearing in a bearing chamber in which the bearing is housed, the lubricating oil is repelled by the high-speed rotating bearing, so that the lubricating oil scatters in the bearing chamber. In this case, there is a concern that the recovery efficiency of the lubricating oil from the bearing chamber may decrease.

[0005] The present disclosure aims to solve the above-described problems.

Means for Solving the Problems

[0006] Aspects of the present disclosure are rotating electric machine systems comprising: a rotating electric machine having a rotor including a permanent magnet and a rotating shaft; a rotating electric machine housing rotatably supporting the rotating shaft; a first bearing and a second bearing interposed between the rotating electric machine housing and the rotating shaft and spaced apart from each other in the axial direction of the rotor, wherein the rotating electric machine system comprises: a first bearing chamber provided in the rotating electric machine housing for housing the first bearing; a first oil nozzle provided in the first bearing chamber and having a first discharge port for discharging lubricating oil toward the first bearing; an oil circulation supply device for recovering the lubricating oil from the first bearing chamber and supplying it to an oil supply passage provided in the rotating electric machine housing; and an oil splash prevention cover provided in the first bearing chamber and covering the first bearing so as to face the first bearing in the axial direction, wherein the first discharge port is located inside the oil splash prevention cover. [Effects of the Invention]

[0007] According to the rotating electric machine system of this disclosure, the scattering of lubricating oil within the first bearing chamber by the high-speed rotating first bearing is prevented, and the stirring up of lubricating oil by the swirling airflow accompanying the rotation of the rotor is also suppressed. As a result, the gas-liquid separation efficiency within the first bearing chamber is improved, and lubricating oil can be recovered efficiently. Furthermore, by reducing the load on the pumps and other equipment used to recover the lubricating oil, it may be possible to contribute to the miniaturization and weight reduction of such pumps and other equipment. [Brief explanation of the drawing]

[0008] [Figure 1] Figure 1 is a perspective view of the combined power system. [Figure 2] Figure 2 is a schematic cross-sectional view of a rotating electric machine system. [Figure 3] Figure 3 is a schematic cross-sectional view of the rotating electric machine system from a different angle. [Figure 4] Figure 4 is an enlarged cross-sectional view of the area around the first bearing. [Figure 5] Figure 5 is an enlarged cross-sectional view of the area around the second bearing. [Figure 6] Figure 6 is a conceptual diagram of an oil circulation supply device in a rotating electric machine system. [Figure 7] Figure 7 is a diagram showing the configuration of the oil splash prevention cover and its surroundings. [Modes for carrying out the invention]

[0009] The combined power system 10 shown in Figure 1 comprises a rotating electric machine system 12 and a gas turbine engine 14 according to this embodiment. The axes of the rotating electric machine system 12 and the gas turbine engine 14 coincide with each other. In other words, the rotating electric machine system 12 and the gas turbine engine 14 are arranged in series on the same axis.

[0010] The combined power system 10 is used as a propulsion power source in, for example, flying objects, ships, or automobiles. Suitable examples of flying objects include drones and multicopters. When mounted on a flying object, the combined power system 10 is used as a power source to rotate, for example, a propeller or a ducted fan. When mounted on a ship, the combined power system 10 is used as a propeller rotation force generator. When mounted on an automobile, the combined power system 10 is used as a power source to rotate a motor.

[0011] The combined power system 10 can also be used as a power source for auxiliary power in aircraft, ships, buildings, etc. Furthermore, the combined power system 10 can also be used as a gas turbine power generation facility. The gas turbine engine 14 is an internal combustion engine.

[0012] In the following explanation, "down" and "up" refer to the lower and upper parts of Figure 2, respectively.

[0013] As shown in Figure 2, the rotating electric machine system 12 comprises a rotating electric machine 16 and a rotating electric machine housing 18. In this embodiment, the rotating electric machine 16 is a generator. The rotating electric machine 16 comprises a rotor 32 and a stator 34.

[0014] The rotating electrical machine housing 18 houses the rotating electrical machine 16. The rotating electrical machine housing 18 includes a main housing 20, a first sub-housing 21, and a second sub-housing 22. The main housing 20 has a substantially cylindrical shape with both ends open. The main housing 20 has a housing chamber 24 for housing the rotating electrical machine 16. A cooling jacket 19 is formed inside the peripheral wall portion of the main housing 20. A liquid refrigerant such as cooling water circulates through the cooling jacket 19.

[0015] The first sub-housing 21 is connected to a first housing end 20a which is an end of the main housing 20 on the X1 direction side, and closes the opening of the first housing end 20a. The second sub-housing 22 is connected to a second housing end 20b which is an end of the main housing 20 on the X2 direction side, and closes the opening of the second housing end 20b.

[0016] The rotor 32 is rotatably supported with respect to the rotating electrical machine housing 18 via a first bearing 38 and a second bearing 40. Therefore, next, the first bearing 38, the second bearing 40, and their peripheral structures will be described.

[0017] As shown in FIG. 4, a hollow cylindrical holder spacer 42 and a hollow cylindrical first bearing holder 44 are inserted into the inner peripheral portion of the first sub-housing 21. The first bearing 38 is disposed inside the first bearing holder 44. The hollow portion of the first sub-housing 21 forms a first bearing chamber 39 for housing the first bearing 38. Lubricating oil LO is supplied to the first bearing 38 through an oil supply hole 42h formed in the holder spacer 42 and an oil supply hole 44h formed in the first bearing holder 44.

[0018] The first bearing holder 44 has a plurality of oil drain holes 440. The plurality of oil drain holes 440 are holes for discharging the lubricating oil LO supplied to the first bearing 38 to the outside of the first bearing holder 44.

[0019] Inside the first bearing holder 44, a spacer ring 46 is fixed. The spacer ring 46 has a plurality of relay holes 46h. The plurality of relay holes 46h are formed at intervals in the circumferential direction of the spacer ring 46.

[0020] The preload applying member 48 applies a load (preload) to the outer ring 382 of the first bearing 38 via the spacer ring 46. The direction of the load is the axial direction (X direction) of the rotor 32. The preload applying member 48 is constituted by, for example, a plurality of disc springs.

[0021] A holder member 50 is attached to the end portion on the X2 direction side of the first bearing holder 44. Since the holder member 50 is fixed to the first bearing holder 44, it is a non-rotating part. The holder member 50 holds the preload applying member 48. The holder member 50 has a hollow cylindrical holder tube portion 51. The preload applying member 48 is disposed in an annular space formed between the first bearing holder 44 and the holder tube portion 51.

[0022] As shown in FIG. 2, an annular second bearing holder 52 is attached to the second housing end 20b (end portion on the X2 direction side) of the main housing 20. The second bearing holder 52 is connected to the main housing 20 via bolts or the like. The outer ring 402 of the second bearing 40 is held by the inner peripheral portion of the second bearing holder 52. A flow path forming member 54 is fixed to the end portion on the X2 direction side of the main housing 20. The flow path forming member 54 covers the second bearing 40. The hollow portion of the flow path forming member 54 forms a second bearing chamber 41 that houses the second bearing 40.

[0023] The rotor 32 has a rotating shaft 58, a sleeve 59, and a permanent magnet 61. The sleeve 59 surrounds the rotating shaft 58, and the permanent magnet 61 surrounds the sleeve 59. A rotor internal flow path 63 is formed in the rotor 32. In this embodiment, lubricating oil LO flows as a liquid refrigerant through the rotor internal flow path 63. The lubricating oil LO flows through the rotor internal flow path 63 from the inlet 631 (see Figure 4) to the outlet 632 (see Figure 5). That is, the lubricating oil LO flows through the rotor internal flow path 63 in the X2 direction. Therefore, with respect to the rotor internal flow path 63, the X1 direction side is upstream and the X2 direction side is downstream. The rotor internal flow path 63 gradually widens in diameter towards the downstream direction.

[0024] The rotating shaft 58 is rotatably supported in the first sub-housing 21 via a first bearing 38 and is also rotatably supported in the main housing 20 via a second bearing 40. The rotating shaft 58 has an inner shaft 60 and an outer shaft 62.

[0025] The inner shaft 60 has a first inner shaft end 60a, which is the end on the X1 direction side, and a second inner shaft end 60b, which is the end on the X2 direction side. The outer shaft 62 has a first outer shaft end 62a, which is the end on the X1 direction side, and a second outer shaft end 62b, which is the end on the X2 direction side. The inner shaft 60 is inserted into the outer shaft 62. The inner shaft 60 is longer than the outer shaft 62.

[0026] The first inner shaft end 60a protrudes from the first outer shaft end 62a in the X1 direction. The first inner shaft end 60a is connected to the first outer shaft end 62a by a fixing structure including a nut member 64, etc.

[0027] A resolver rotor 66a is fixed to the first inner shaft end 60a. A resolver stator 66b is positioned to surround the resolver rotor 66a. The resolver stator 66b is held by a resolver holder 68 mounted on the first sub-housing 21. The resolver rotor 66a and the resolver stator 66b constitute the resolver 66.

[0028] The outer shaft 62 is a hollow cylindrical member. As shown in Figure 4, the outer shaft 62 forms a rotor internal flow path 63 between the fastening ring 70, the first bearing 38, the support member 72, and the sleeve 59.

[0029] As shown in Figure 4, the inner ring 381 of the first bearing 38 is supported by the first shaft portion 62A, which constitutes the X1 direction end of the outer shaft 62. The outer circumference of the first shaft portion 62A has a male screw 621 and a plurality of flow channel grooves 622.

[0030] A fastening ring 70 is screwed onto the male thread 621 of the first shaft portion 62A. The fastening ring 70 constitutes part of the rotor 32. The inner ring 381 of the first bearing 38 is sandwiched between the fastening ring 70 and the support member 72 in the axial direction (X direction) of the rotor 32. The support member 72 is an inner ring stopper. As a result, the inner ring 381 of the first bearing 38 is fixed at a predetermined location on the outer circumferential surface of the outer shaft 62.

[0031] The fastening ring 70 has a plurality of communication holes 70h formed at intervals from each other in the circumferential direction. The plurality of communication holes 70h penetrate the inner circumference of the fastening ring 70 in the axial direction. The annular opening 701 provided on the X1 direction side of the fastening ring 70 is the inlet 631 of the rotor internal flow path 63. The end face of the fastening ring 70 on the X2 direction side abuts against the inner ring 381 of the first bearing 38. The plurality of communication holes 70h constitute a part of the rotor internal flow path 63.

[0032] The multiple flow channel grooves 622 are located downstream of the multiple communication holes 70h formed in the fastening ring 70. The multiple flow channel grooves 622 are formed at intervals from each other in the circumferential direction of the outer shaft 62. Each flow channel groove 622 is recessed radially inward from the outer circumferential surface of the outer shaft 62 and extends in the axial direction of the rotor 32. The multiple flow channel grooves 622 constitute a part of the internal flow channel 63 of the rotor. The inner ring 381 of the first bearing 38 is positioned to surround the multiple flow channel grooves 622.

[0033] The support member 72 is an annular member positioned between the inner ring 381 of the first bearing 38 and the sleeve 59. A portion of the rotor internal flow path 63 is formed between the outer shaft 62 and the support member 72. The support member 72 is fixed to the outer shaft 62, for example, by press-fitting. The support member 72 is supported by the outer circumference of the outer shaft 62. The support member 72 is positioned to surround a plurality of flow grooves 622. The support member 72 is adjacent to the inner ring 381 of the first bearing 38 and supports the first sleeve end 59a, which is one end of the sleeve 59. A portion of the rotor internal flow path 63 is formed between the outer shaft 62 and the sleeve 59.

[0034] As shown in Figure 5, an outlet space 63e of the rotor internal flow path 63 is formed between the outer shaft 62 and the second sleeve end 59b.

[0035] The inner ring stopper 76, the inner ring 401 of the second bearing 40, and the outer ring stopper 78 are supported by the outer circumferential surface of the outer shaft 62. The inner ring 401 of the second bearing 40 is sandwiched between the inner ring stopper 76 and the outer ring stopper 78 from both axial sides. This fixes the inner ring 401 of the second bearing 40 to a predetermined location on the outer circumferential surface of the outer shaft 62.

[0036] As shown in Figure 2, the sleeve 59 is a hollow cylindrical member having an inner bore 59h. The rotating shaft 58 is inserted into the inner bore 59h of the sleeve 59. The majority of the rotor's internal flow path 63 is formed by the sleeve 59 and the rotating shaft 58. The sleeve 59 surrounds the rotating shaft 58.

[0037] As shown in Figure 4, a sealing portion 82 is provided on the outer circumference of the first sleeve end 59a. The sealing portion 82 is a labyrinth seal having a plurality of protrusions spaced apart from each other in the axial direction.

[0038] The holder member 50 is a hollow cylindrical portion positioned radially outward from the first sleeve end 59a. Therefore, the holder member 50 faces the seal portion 82 in the radial direction and surrounds the seal portion 82. A gap is formed between the seal portion 82 and the holder member 50 (holder cylindrical portion 51). The preloading member 48 is positioned to surround the holder member 50, the seal portion 82, and the support member 72. The first sleeve end 59a is inserted inside the holder member 50. An annular gap 49 is formed between the first sleeve end 59a and the holder member 50.

[0039] The sleeve 59 is fixed to the outer surface of the rotating shaft 58, for example, by shrink fitting. The sleeve 59 holds a permanent magnet 61. In this embodiment, the rotor 32 is a so-called SPM type, in which the permanent magnet 61 is arranged on the outer circumferential surface of the sleeve 59. Alternatively, the rotor 32 may be a so-called IPM type, in which the permanent magnet 61 is embedded in the sleeve 59.

[0040] As shown in Figure 2, the first ring body 84 is in contact with the end face of the permanent magnet 61 on the X1 direction side. The second ring body 86 is in contact with the end face of the permanent magnet 61 on the X2 direction side. The first ring body 84, the permanent magnet 61, and the second ring body 86 are sandwiched between a pair of magnet stoppers 88 and 90 in the axial direction of the rotor 32. Hereinafter, the magnet stopper 88 on the X1 direction side will be referred to as the "first magnet stopper 88," and the magnet stopper 90 on the X2 direction side will be referred to as the "second magnet stopper 90."

[0041] The first magnet stopper 88 is fixed to the sleeve 59 by a fixing ring 92 (see Figure 4) that is screwed onto the sleeve 59. The second magnet stopper 90 is fixed to the second sleeve end 59b (see Figure 5). The second sleeve end 59b is the other end of the sleeve 59 in the axial direction. The first magnet stopper 88 and the second magnet stopper 90 are fixed to the outer circumference of the sleeve 59, for example, by shrink fitting. This fixes the permanent magnet 61 to the outer surface of the sleeve 59.

[0042] As shown in Figure 5, a sealing portion 94 is provided on the outer circumference of the second magnet stopper 90. The sealing portion 94 is a labyrinth seal having a plurality of protrusions spaced apart from each other in the axial direction. The sealing portion 94 faces radially toward an annular projection 96 provided on the main housing 20. A gap is formed between the sealing portion 94 and the annular projection 96.

[0043] The second sleeve end 59b forms an outlet space 63e of the rotor internal flow path 63 between itself and the outer shaft 62. The inner diameter of the second sleeve end 59b increases as it moves toward the X2 direction. The downstream end of the outlet space 63e (the opening of the sleeve 59 on the X2 direction side) is the outlet 632 of the rotor internal flow path 63.

[0044] As shown in Figure 2, the stator 34 has a stator core 340 and a plurality of electromagnetic coils 341. The stator core 340 is a cylindrical member. The stator core 340 is constructed, for example, by stacking a plurality of ring-shaped electromagnetic steel sheets in the axial direction. Multiple slots are formed in the stator core 340. Teeth are formed between adjacent slots.

[0045] The multiple electromagnetic coils 341 include U-phase coils, V-phase coils, and W-phase coils. Therefore, when the rotating electric machine 16 is a generator, the rotating electric machine 16 is a so-called three-phase power supply. Each of the multiple electromagnetic coils 341 is constructed by winding a conductor around the teeth of the stator core 340.

[0046] As shown in Figure 1, a terminal casing 98 is integrally provided on the upper surface of the main housing 20 on the X1 direction side. As shown in Figure 2, the terminal casing 98 houses the U-phase terminal 100a, the V-phase terminal 100b, and the W-phase terminal 100c. The U-phase terminal 100a, the V-phase terminal 100b, and the W-phase terminal 100c are electrically connected to the U-phase coil, V-phase coil, and W-phase coil of the stator 34, respectively.

[0047] As shown in Figure 2, the rotating electric machine system 12 is further provided with a gas refrigerant flow path structure 102. The gas refrigerant flow path structure 102 is a structure for circulating gas through the rotor 32 (particularly the permanent magnet 61) and the stator 34. At this time, the rotor 32 and stator 34 can be cooled by the cooling gas. In the following description, air will be used as an example of the cooling gas. The air is supplied from the gas supply device 103. As will be described later, the air supplied to the rotating electric machine housing 18 forms an air curtain to prevent lubricating oil LO from entering the containment chamber 24. For this reason, the gas refrigerant flow path structure 102 also serves as a sealing air flow path structure.

[0048] The gas refrigerant flow path structure 102 includes a gas supply passage 104, a first branch passage 105, and a second branch passage 106. An air inlet, which serves as the inlet to the gas supply passage 104, is provided on the outer surface of the first sub-housing 21. The first branch passage 105 and the second branch passage 106 are part of the containment chamber 24.

[0049] The gas supply passage 104 is formed in the first sub-housing 21. The air that has passed through the gas supply passage 104 flows into the containment chamber 24 of the main housing 20. The air that has flowed into the containment chamber 24 is divided by the first branch passage 105 and the second branch passage 106.

[0050] The first branch passage 105 is a passage that directs air toward the first bearing 38. As shown in Figure 4, the air that has passed through the first branch passage 105 flows into the annular gap 49 formed between the holder member 50 and the sleeve 59, and flows through this annular gap 49 in the X1 direction. The air that flows toward the first bearing 38 in this way forms an air curtain. The air curtain prevents lubricating oil LO from entering the housing chamber 24 that houses the rotor 32. Subsequently, the air flows through the relay hole 46h provided in the spacer ring 46 into the passage 116 formed in the first sub-housing 21. As shown in Figure 2, the air that has passed through the passage 116 flows into the first bearing chamber 39, which is the hollow part of the first sub-housing 21.

[0051] As shown in Figure 3, air is discharged from the first bearing chamber 39 via a gas discharge passage 107 (hereinafter referred to as the "first gas discharge passage 107"). The first gas discharge passage 107 is formed in the first sub-housing 21. The gas inlet (first vent opening 107a) of the first gas discharge passage 107 is formed in the upper part of the first bearing chamber 39. In reference to the first bearing chamber 39, "upper part" means the region of the first bearing chamber 39 above the axis of the rotating electric machine system 12 (the rotation axis Ax of the rotor 32). Therefore, the first vent opening 107a may be formed below the uppermost part of the first bearing chamber 39. The air discharged via the first gas discharge passage 107 is introduced into a tank 144 (see Figure 6).

[0052] The second branch passage 106 is a clearance between the rotor 32 and the stator 34 that extends along the axial direction of the rotor 32. The second branch passage 106 is a passage that directs air toward the second bearing 40. As shown in Figure 5, a portion of the air that has passed through the second branch passage 106 flows into the outer circumference of the inner ring stopper 76 and toward the second bearing 40. The air flowing toward the second bearing 40 in this way forms an air curtain. The air curtain prevents lubricating oil LO from entering the housing chamber 24 that houses the rotor 32.

[0053] As shown in Figure 2, the remaining air that has passed through the second branch passage 106 flows into the air distribution passage 118 formed in the main housing 20. The air that has passed through the air distribution passage 118 flows into the flow path 55 formed between the second sub-housing 22 and the flow path forming member 54. The outer circumference of the flow path forming member 54 is fixed to the main housing 20 inside the second sub-housing 22. As shown in Figure 5, an annular ventilation passage 56 is formed between the inner circumference of the flow path forming member 54 and the outer circumference of the outer inner ring stopper 78. The air that has passed through the flow path 55 flows into the second bearing chamber 41 via the flow path 55 and the ventilation passage 56 and heads toward the second bearing 40.

[0054] As shown in Figure 3, air is discharged from the second bearing chamber 41 via a gas discharge passage 108 (hereinafter referred to as the "second gas discharge passage 108") formed in the rotating electric machine housing 18. The gas inlet (second vent opening 108a) of the second gas discharge passage 108 is formed in the upper part of the second bearing chamber 41. In the case of the second bearing chamber 41, "upper part" refers to the region of the second bearing chamber 41 above the rotation axis Ax of the rotor 32. Therefore, the second vent opening 108a may be formed below the uppermost part of the second bearing chamber 41. The air discharged via the second gas discharge passage 108 is introduced into a tank 144 (see Figure 6).

[0055] As shown in Figure 3, the rotating electric machine system 12 is further provided with a lubricating oil flow path structure 130 and a rotor cooling structure 150. The lubricating oil flow path structure 130 is a flow path for supplying lubricating oil LO to the first bearing 38 and the second bearing 40.

[0056] The lubrication oil flow path structure 130 includes a lubrication oil introduction passage 132, a first distribution passage 134, a first drain passage 110 (Figure 2), a second distribution passage 136, and a second drain passage 114 (Figure 2). The lubrication oil introduction passage 132, the first distribution passage 134, and the second distribution passage 136 are oil supply passages 131 provided in the rotating electric machine housing 18. Lubrication oil LO is supplied from the oil circulation supply device 140 to the lubrication oil introduction passage 132. Inside the first sub-housing 21, the lubrication oil introduction passage 132 branches into the first distribution passage 134 and the second distribution passage 136.

[0057] The first distribution channel 134 is formed in the first sub-housing 21. Lubricating oil LO is supplied to the first bearing 38 via the first distribution channel 134. The first distribution channel 134 has a first line 134a and a second line 134b. The first line 134a is a flow path that supplies lubricating oil LO toward the outer circumference of the first bearing 38. The second line 134b is a flow path that supplies lubricating oil LO toward the end face 38e on the X1 direction side of the first bearing 38.

[0058] The second line 134b is formed in the first oil nozzle 138. The first oil nozzle 138 is fixed to the first sub-housing 21 and is located in the first bearing chamber 39. One end of the first oil nozzle 138 is fixed to the first sub-housing 21. The first oil nozzle 138 extends toward the rotor 32 (see also Figure 7). The other end of the first oil nozzle 138 is provided with a first discharge port 138a that discharges lubricating oil LO toward the end face 38e of the first bearing 38. The first discharge port 138a is located near the end face 38e of the first bearing 38 and faces the end face 38e.

[0059] As shown in Figure 2, the lubricating oil LO supplied to the first bearing 38 is discharged from the first bearing chamber 39 via a first drain passage 110 formed in the rotating electric machine housing 18. The upstream end of the first drain passage 110 is an oil outlet 111 (hereinafter referred to as "first oil outlet 111") that discharges the lubricating oil LO from the first bearing chamber 39. The first oil outlet 111 is located at the bottom of the first bearing chamber 39. The first oil outlet 111 only needs to be positioned in a location that can draw in the lubricating oil LO stored in the first bearing chamber 39. For this reason, the first oil outlet 111 does not need to be at the very bottom of the first bearing chamber 39.

[0060] Furthermore, as described above, an air curtain is formed in the vicinity of the first bearing 38. This prevents the lubricating oil LO supplied to the first bearing 38 from entering the housing chamber 24 through the annular gap 49 (see Figure 4).

[0061] As shown in Figure 3, the second distribution channel 136 of the lubricating oil flow path structure 130 is formed in the main housing 20. The lubricating oil LO is supplied to the second bearing 40 via the second distribution channel 136. The lubricating oil LO supplied to the second bearing 40 is discharged from the second bearing chamber 41 via the second drain channel 114 formed in the rotating electric machine housing 18.

[0062] As shown in Figure 2, the upstream end of the second drain passage 114 is an oil outlet 115 (hereinafter referred to as "second oil outlet 115") that discharges lubricating oil LO from the second bearing chamber 41. The second oil outlet 115 is located at the bottom of the second bearing chamber 41. The second oil outlet 115 only needs to be positioned in a location that can draw in the lubricating oil LO stored in the second bearing chamber 41. For this reason, the second oil outlet 115 does not need to be at the very bottom of the second bearing chamber 41.

[0063] Furthermore, as described above, an air curtain is formed in the vicinity of the second bearing 40. This prevents the lubricating oil LO supplied to the second bearing 40 from entering the containment chamber 24.

[0064] As shown in Figure 3, the rotor cooling structure 150 is a flow path for supplying lubricating oil LO into the rotor 32 and cooling the permanent magnet 61. The rotor cooling structure 150 includes a supply passage 152 and the rotor internal flow path 63 and second drain passage 114 described above. The supply passage 152 supplies lubricating oil LO to the rotor internal flow path 63. The supply passage 152 has an introduction passage 152a formed in the first sub-housing 21 and a guide passage 152b formed in the second oil nozzle 153.

[0065] The guide channel 152b is in communication with the introduction channel 152a. The second oil nozzle 153 is located in the first bearing chamber 39. One end of the second oil nozzle 153 is fixed to the first sub-housing 21. The second oil nozzle 153 extends toward the rotor 32 (see also Figure 7). The other end of the second oil nozzle 153 has a second discharge port 153a, which is the exit of the guide channel 152b. The second discharge port 153a is near the inlet 631 (see Figure 4) of the rotor internal flow path 63 and faces the inlet 631. The lubricating oil LO discharged from the second discharge port 153a flows into the rotor internal flow path 63 through the annular opening 701 (inlet 631) of the fastening ring 70, as shown in Figure 4.

[0066] As shown in Figure 6, the rotating electric machine system 12 is further provided with an oil circulation supply device 140. The oil circulation supply device 140 recovers lubricating oil LO from the first bearing chamber 39 and the second bearing chamber 41, and supplies lubricating oil LO to an oil supply passage 131 provided in the rotating electric machine housing 18. The oil circulation supply device 140 comprises a recovery pump 142, a tank 144, a supply pump 146, and a gas-liquid separator 148. Driven by the recovery pump 142, lubricating oil LO is drawn from the first bearing chamber 39 and the second bearing chamber 41 via the first drain passage 110 and the second drain passage 114. The drawn lubricating oil LO flows into the tank 144 via the recovery line 141.

[0067] Tank 144 stores the lubricating oil LO discharged (recovered) from the first bearing chamber 39 and the second bearing chamber 41. Air discharged from the first bearing chamber 39 and the second bearing chamber 41 is also introduced into Tank 144 via the first gas discharge passage 107 and the second gas discharge passage 108. The air discharged from the first bearing chamber 39 and the second bearing chamber 41 is a gas-liquid mixed fluid containing the mist-like lubricating oil LO. Therefore, the gas-liquid mixed fluid flowing into Tank 144 is separated into gas and liquid components within Tank 144. In other words, Tank 144 has a gas-liquid separation function. The air is discharged from Tank 144 and introduced into the gas-liquid separator 148. After further gas-liquid separation in the gas-liquid separator 148, the air is released into the atmosphere.

[0068] The supply pump 146 draws lubricating oil LO from the tank 144 and supplies the lubricating oil LO to the oil supply passage 131 of the rotating electric machine housing 18 via the supply line 149. In this way, the oil circulation supply device 140 supplies lubricating oil LO to the oil supply passage 131 of the rotating electric machine housing 18, and also recovers lubricating oil LO from the rotating electric machine housing 18 and supplies the lubricating oil LO back to the oil supply passage 131, performing an oil circulation operation.

[0069] As shown in Figures 2 and 3, the rotating electric machine system 12 further includes an oil splash prevention cover 170. The oil splash prevention cover 170 is located inside the first bearing chamber 39. The oil splash prevention cover 170 covers the first bearing 38 so as to face it in the axial direction. The oil splash prevention cover 170 is fixed to the first sub-housing 21. Therefore, the oil splash prevention cover 170 is a non-rotating member.

[0070] During operation of the rotating electric machine system 12, the lubricating oil LO discharged from the first oil nozzle 138 is repelled by the high-speed rotating bearing. Similarly, the lubricating oil LO discharged from the second oil nozzle 153 is repelled by the fastening ring 70 that is screwed onto the high-speed rotating rotor 32. The oil splash prevention cover 170 prevents the lubricating oil LO that is thus repelled from scattering within the first bearing chamber 39.

[0071] The oil splash prevention cover 170 has a base wall portion 172 and a peripheral wall portion 174. The base wall portion 172 faces the first bearing 38 in the axial direction of the rotating electric machine system 12. A through hole 173 is formed in the base wall portion 172. The rotor 32 is inserted through the through hole 173. The through hole 173 is a circular opening. The diameter of the through hole 173 is slightly larger than the outer diameter of the portion of the rotor 32 that is inserted into the through hole 173. Therefore, an annular gap is formed between the inner circumferential end of the base wall portion 172 (the edge portion that forms the through hole 173) and the rotor 32. The peripheral wall portion 174 protrudes axially (in the X2 direction) from the outer circumference of the base wall portion 172.

[0072] As shown in Figure 3, the first oil nozzle 138 protrudes from the inner circumferential surface of the oil splash prevention cover 170. The first oil nozzle 138 is connected to the circumferential wall portion 174. The first oil nozzle 138 is inserted into the first insertion hole 175a formed in the circumferential wall portion 174. The first discharge port 138a is located inside the oil splash prevention cover 170.

[0073] The second oil nozzle 153 protrudes from the inner circumferential surface of the oil splash prevention cover 170. The second oil nozzle 153 is connected to the circumferential wall portion 174. The second oil nozzle 153 is inserted into a second insertion hole 175b formed in the circumferential wall portion 174. The second discharge port 153a is located inside the oil splash prevention cover 170. Note that the first oil nozzle 138, the second oil nozzle 153, and the oil splash prevention cover 170 may be a single part formed by integral molding.

[0074] As shown in Figure 2, the oil splash prevention cover 170 has an opening 176 that opens downward. The opening 176 is formed at the bottom of the oil splash prevention cover 170. The opening 176 guides (directs) the lubricating oil LO that has collided with the inner surface of the oil splash prevention cover 170 downward. As a result, the lubricating oil LO that flows out of the oil splash prevention cover 170 through the opening 176 is stored at the bottom of the first bearing chamber 39. The lubricating oil LO is sucked in by the first oil outlet 111 and discharged from the first bearing chamber 39.

[0075] The first oil outlet 111 is located below the opening 176. As shown in Figures 2 and 7, the first oil outlet 111 is located directly below the opening 176. Alternatively, the first oil outlet 111 may be located at a position horizontally offset from directly below the opening 176. The first oil outlet 111 only needs to be positioned in a location that allows it to draw in lubricating oil LO.

[0076] As shown in Figure 7, the first bearing chamber 39 is provided with a wall portion 186 that suppresses the uplift (rise) of lubricating oil LO due to the airflow (swirling airflow) generated within the first bearing chamber 39. The wall portion 186 is provided on the outside of the oil splash prevention cover 170. The wall portion 186 protrudes from the inner circumferential surface 39s of the first bearing chamber 39 (the inner circumferential surface of the first sub-housing 21).

[0077] In this embodiment, the wall portion 186 is part of the restraining member 180. The restraining member 180 is fixed to the first sub-housing 21. The restraining member 180 has a fixed base portion 182, a support portion 184, and a wall portion 186. The fixed base portion 182 is fixed to the first sub-housing 21.

[0078] The support portion 184 is a bent portion relative to the fixed base portion 182 and protrudes axially from the fixed base portion 182. The support portion 184 supports the wall portion 186. The wall portion 186 is bent relative to the support portion 184. The wall portion 186 protrudes from the support portion 184 toward the oil splash prevention cover 170. In this case, the wall portion 186 protrudes from the peripheral wall portion 174 of the oil splash prevention cover 170 toward the inner circumferential surface 39s of the first bearing chamber 39.

[0079] Next, we will describe the gas turbine engine 14 shown in Figure 1. Note that the configuration of the gas turbine engine 14 is similar to that shown in Figure 7 of Japanese Patent Publication No. 2023-106078. Therefore, the description of the gas turbine engine 14 will be brief.

[0080] The gas turbine engine 14 includes an engine housing 160. The engine housing 160 is connected to a rotating electric machine housing 18. The engine housing 160 has a plurality of legs 166. An intake space is formed between the plurality of legs 166.

[0081] As shown in Figure 2, the gas turbine engine 14 includes an output shaft 168. A compressor wheel (not shown) and a turbine wheel (not shown) are mounted radially outward from the output shaft 168. The output shaft 168 is connected to a rotary shaft 58. The compressor wheel and turbine wheel are rotatable integrally with the rotary shaft 58 and the output shaft 168.

[0082] The gas turbine engine 14 may be a gas supply device 103 that supplies air to the gas refrigerant flow path structure 102 (seal air flow path structure). In this case, a portion of the air generated by the rotation of the compressor wheel is extracted and supplied to the gas supply passage 104 provided in the first sub-housing 21. The gas supply device 103 may also be another compressor that compresses atmospheric air and supplies it to the gas supply passage 104. The cooling gas supplied to the gas supply passage 104 may be a gas supplied from an oxygen cylinder or a nitrogen cylinder, etc.

[0083] The combined power system 10 configured as described above operates as follows.

[0084] First, the gas turbine engine 14 is started by the drive of the rotating electric machine 16. Once the gas turbine engine 14 is started, the rotor 32 of the rotating electric machine 16 rotates due to the rotational driving force of the output shaft 168 of the gas turbine engine 14, and the rotating electric machine 16 generates electricity. This brings the combined power system 10 into operation.

[0085] As shown in Figure 6, during operation of the combined power system 10, air is supplied to the rotating electric machine housing 18 from the gas supply device 103. This cools the rotating electric machine 16 and seals it with an air curtain. In addition, lubricating oil LO is supplied from the oil circulation supply device 140 to the oil supply passage 131 of the rotating electric machine housing 18, and lubricating oil LO is supplied to the first bearing 38 and the second bearing 40. In this case, as shown in Figure 2, the first oil nozzle 138 discharges lubricating oil LO toward the first bearing 38.

[0086] Lubricating oil LO is supplied from the oil circulation supply device 140 to the second oil nozzle 153, and lubricating oil LO is discharged from the second oil nozzle 153 toward the rotor 32 (inlet 631 of the rotor internal flow path 63). As a result, the permanent magnet 61 is cooled by the lubricating oil LO flowing through the rotor internal flow path 63.

[0087] In this manner, lubricating oil LO is discharged from the first oil nozzle 138 toward the first bearing 38, and lubricating oil LO is discharged from the second oil nozzle 153 toward the rotor 32. In this case, the lubricating oil LO is repelled by the high-speed rotating rotor 32 and the first bearing 38, but the oil splash prevention cover 170 prevents the lubricating oil LO from splashing within the first bearing chamber 39. Specifically, the repelled lubricating oil LO collides with the inner surface of the oil splash prevention cover 170 (inner surface of the cover), flows down along the inner surface of the cover due to gravity, and reaches the oil storage area provided at the bottom of the first bearing chamber 39 through the opening 176. The lubricating oil LO is sucked in at the first oil outlet 111 and discharged from the first bearing chamber 39.

[0088] Within the first bearing chamber 39, a swirling airflow is generated as the rotor 32 rotates, but the wall 186 suppresses the uplift of the lubricating oil LO. In other words, the wall 186 blocks the rise of the lubricating oil LO due to the swirling airflow, so the lubricating oil LO can be retained in the lower part of the first bearing chamber 39. The wall 186 also has the function of reducing the flow velocity of the swirling airflow.

[0089] On the other hand, as shown in Figure 6, air is discharged from the first bearing chamber 39 via the first gas discharge passage 107. In this way, the fluid in the first bearing chamber 39 is separated into lubricating oil LO and air, and each is discharged from the first bearing chamber 39. That is, the first bearing chamber 39 functions as the first gas-liquid separation unit. In the tank 144, the air discharged from the first bearing chamber 39 is introduced, and gas-liquid separation is performed again. For this reason, the tank 144 functions as the second gas-liquid separation unit. The air discharged from the tank 144 is subjected to gas-liquid separation again by the gas-liquid separator 148. For this reason, the gas-liquid separator 148 functions as the third gas-liquid separation unit.

[0090] This embodiment provides the following effects.

[0091] The rotating electric machine system 12 is equipped with an oil splash prevention cover 170 located inside the first bearing chamber 39. The first discharge port 138a of the first oil nozzle 138 is positioned inside the oil splash prevention cover 170. With this configuration, the lubricating oil LO that is repelled by the high-speed rotating first bearing 38 is prevented from scattering inside the first bearing 38, and the stirring up of the lubricating oil LO by the swirling airflow is also suppressed. As a result, the gas-liquid separation efficiency in the first bearing chamber 39 is improved, and the lubricating oil LO can be recovered efficiently. In addition, the load on the pumps used to recover the lubricating oil LO is reduced, which can contribute to the miniaturization and weight reduction of the pumps.

[0092] Specifically, the load on the recovery pump 142 is reduced, which can contribute to miniaturizing and lightening the recovery pump 142. Also, the improved gas-liquid separation function in the first bearing chamber 39 means that a large gas-liquid separation function is not required for the tank 144, which can contribute to miniaturizing the tank 144. The improved gas-liquid separation function in the first bearing chamber 39 can also contribute to miniaturizing the gas-liquid separator 148 located downstream of the tank 144. Furthermore, if sufficient gas-liquid separation is achieved by the first bearing chamber 39 and the tank 144, the gas-liquid separator 148 can be eliminated.

[0093] The first oil nozzle 138 protrudes from the inner circumferential surface of the oil splash prevention cover 170. With this configuration, the first discharge port 138a can be positioned near the first bearing 38 while the first bearing 38 can be sufficiently covered by the oil splash prevention cover 170, thereby improving both the supply efficiency of lubricating oil LO to the first bearing 38 and the oil splash prevention function.

[0094] The oil splash prevention cover 170 has a base wall portion 172 facing the first bearing 38 in the axial direction, and a peripheral wall portion 174 that protrudes axially from the outer circumference of the base wall portion 172. With this configuration, the first bearing 38 is well covered within the first bearing chamber 39, thereby effectively preventing the splashing of lubricating oil LO.

[0095] The first oil nozzle 138 is connected to the peripheral wall portion 174. With this configuration, the first oil nozzle 138 and the oil splash prevention cover 170 can be compactly arranged within the first bearing chamber 39.

[0096] The oil splash prevention cover 170 has an opening 176 that opens downwards. With this configuration, the lubricating oil LO can be efficiently recovered by collecting it at the bottom of the first bearing chamber 39.

[0097] The first bearing chamber 39 is provided with a first oil outlet 111 below the opening 176 for discharging lubricating oil LO from the first bearing chamber 39. With this configuration, the lubricating oil LO collected at the bottom of the first bearing chamber 39 can be efficiently recovered.

[0098] As shown in Figure 7, the first bearing chamber 39 is provided with a wall portion 186 on the outside of the oil splash prevention cover 170 to suppress the uplift of lubricating oil LO by the airflow generated within the first bearing chamber 39. With this configuration, the uplift of lubricating oil LO by the airflow generated within the first bearing chamber 39 is suppressed, so that the lubricating oil LO collected at the bottom of the first bearing chamber 39 can be recovered more efficiently.

[0099] The wall portion 186 protrudes from the inner circumferential surface of the first bearing chamber 39. With this configuration, the scraping up of lubricating oil LO by the airflow generated in the first bearing chamber 39 can be effectively suppressed.

[0100] As shown in Figure 3, a second oil nozzle 153 is provided in the first bearing chamber 39, having a second discharge port 153a that discharges lubricating oil LO toward the inlet 631 (Figure 4) of the rotor internal flow path 63. The second discharge port 153a is located inside the oil splash prevention cover 170. With this configuration, the permanent magnet 61 can be cooled by the lubricating oil LO supplied into the rotor 32. In addition, by preventing the splashing of lubricating oil LO that is repelled by the periphery of the inlet 631 of the rotor internal flow path 63, the lubricating oil LO can be recovered efficiently.

[0101] As shown in Figure 6, the oil circulation supply device 140 recovers the lubricating oil LO discharged from the rotating electric machine housing 18 via the first oil outlet 111 and the cooling gas (air) discharged from the rotating electric machine housing 18 via the first gas outlet 107 using the tank 144. The oil circulation supply device 140 then resupplies the lubricating oil LO recovered by the tank 144 to the oil supply passage 131 of the rotating electric machine housing 18. With this configuration, the lubricating oil LO and the cooling gas are separated into gas-liquid and gas-liquid components in the first bearing chamber 39, thus reducing the load on the pumps and other equipment used to recover the lubricating oil LO (recovery pump 142, tank 144, supply pump 146, gas-liquid separator 148). Furthermore, since the lubricating oil LO mixed into the second gas outlet 108 by the airflow of the cooling gas can be recovered into the tank 144, the recovery efficiency of the lubricating oil LO can be improved.

[0102] The following additional information is disclosed regarding the above embodiments.

[0103] (Note 1) The rotating electric machine system (12) of the present disclosure comprises: a rotating electric machine (16) having a rotor (32) including a permanent magnet (61) and a rotating shaft (58); a rotating electric machine housing (18) that rotatably supports the rotating shaft; and a first bearing (38) and a second bearing (40) interposed between the rotating electric machine housing and the rotating shaft and spaced apart from each other in the axial direction of the rotor, wherein the rotating electric machine housing is provided with a first bearing chamber (39) for housing the first bearing, and The system includes a first oil nozzle (138) provided in the first bearing chamber and having a first discharge port (138a) for discharging lubricating oil (LO) toward the first bearing; an oil circulation supply device (140) for recovering the lubricating oil from the first bearing chamber and supplying it to an oil supply passage (131) provided in the rotating electric machine housing; and an oil splash prevention cover (170) provided in the first bearing chamber and covering the first bearing so as to face the first bearing in the axial direction, wherein the first discharge port is located inside the oil splash prevention cover. With this configuration, it is prevented that lubricating oil repelled by the high-speed rotating first bearing will be scattered within the first bearing, and the stirring up of lubricating oil by the swirling airflow accompanying the rotation of the rotor is also suppressed. As a result, the gas-liquid separation efficiency in the first bearing chamber is improved, and lubricating oil can be recovered efficiently. Furthermore, by reducing the load on the pumps used to recover the lubricating oil, it is possible to contribute to the miniaturization and weight reduction of the pumps, etc.

[0104] (Note 2) In the rotating electric machine system described in Note 1, the first oil nozzle may protrude from the inner circumferential surface of the oil splash prevention cover. With this configuration, the first discharge port can be positioned near the first bearing while the first bearing can be sufficiently covered by the oil splash prevention cover, thereby improving both the efficiency of lubricating oil supply to the first bearing and the oil splash prevention function.

[0105] (Note 3) In the rotating electric machine system described in Note 1, the oil splash prevention cover may have a base wall portion (172) facing the first bearing in the axial direction and a peripheral wall portion (174) protruding in the axial direction from the outer circumference of the base wall portion. With such a configuration, the scattering of lubricating oil can be effectively prevented by covering the first bearing well within the first bearing chamber.

[0106] (Note 4) In the rotating electric machine system described in Note 3, the first oil nozzle may be connected to the peripheral wall portion. With this configuration, the first oil nozzle and the oil splash prevention cover can be compactly arranged in the first bearing chamber.

[0107] (Note 5) In the rotating electric machine system described in Note 1, the oil splash prevention cover may have an opening (176) that opens downward. With such a configuration, the lubricating oil can be efficiently recovered by collecting it at the bottom of the first bearing chamber.

[0108] (Note 6) In the rotating electric machine system described in Note 5, the first bearing chamber may be provided with an oil outlet (111) below the opening for discharging the lubricating oil from the first bearing chamber. With this configuration, the lubricating oil collected at the bottom of the first bearing chamber can be efficiently recovered.

[0109] (Note 7) In the rotating electric machine system described in Note 1, the first bearing chamber may be provided with a wall portion (186) on the outside of the oil splash prevention cover to suppress the stirring up of the lubricating oil by the airflow generated in the first bearing chamber. With such a configuration, the stirring up of the lubricating oil by the airflow generated in the first bearing chamber is suppressed, so that the lubricating oil collected at the bottom of the first bearing chamber can be recovered more efficiently.

[0110] (Note 8) In the rotating electric machine system described in Note 7, the wall portion may protrude from the inner circumferential surface of the first bearing chamber. With this configuration, the stirring up of the lubricating oil by the airflow generated in the first bearing chamber can be effectively suppressed.

[0111] (Note 9) In the rotating electric machine system described in Note 1, a rotor internal passage (63) for circulating the lubricating oil is formed inside the rotor, the rotor has an inlet (631) for the rotor internal passage, the inlet of the rotor internal passage opens in the first bearing chamber, and a second oil nozzle (153) having a second discharge port (153a) for discharging the lubricating oil toward the inlet is provided inside the first bearing chamber, and the second discharge port may be located inside the oil splash prevention cover. With this configuration, the permanent magnet can be cooled by the lubricating oil supplied into the rotor. In addition, the lubricating oil can be efficiently recovered by preventing splashing of the lubricating oil that is repelled by the periphery of the second discharge port.

[0112] (Note 10) In the rotating electric machine system described in any one of Notes 1 to 9, the rotating electric machine housing has a gas supply passage (104) for supplying cooling gas into the rotating electric machine housing and a gas discharge passage (107) for discharging the cooling gas from the first bearing chamber, and the oil circulation supply device has a tank (144) for recovering the lubricating oil discharged from the rotating electric machine housing via the oil discharge passage and the cooling gas discharged from the rotating electric machine housing via the gas discharge passage, and the lubricating oil recovered by the tank may be supplied again to the oil supply passage of the rotating electric machine housing. With this configuration, the lubricating oil and cooling gas are separated into gas-liquid forms in the first bearing chamber, so the load on the pump and other equipment used to recover the lubricating oil can be reduced. In addition, since the lubricating oil mixed into the gas discharge passage by the airflow of the cooling gas can be recovered in the tank, the recovery efficiency of the lubricating oil can be improved.

[0113] While this disclosure has been described in detail, it is not limited to the individual embodiments described above. These embodiments can be added, replaced, modified, partially deleted, etc., in any way that does not depart from the gist of this disclosure or from the spirit of this disclosure derived from the claims and their equivalents. These embodiments can also be implemented in combination. For example, the order of operations and processes in the embodiments described above are given as examples only and are not limited thereto. The same applies when numerical values ​​or mathematical formulas are used in the description of the embodiments described above. [Explanation of Symbols]

[0114] 12…Rotating Electrical Machine System 16…Rotating Electrical Machine 18... Rotating electric machine housing 38... First bearing 39...First bearing chamber 63...Rotor internal flow path 111...Oil drain port 115...Oil drain port 138...First oil nozzle 140...Oil circulation supply device 170... Oil splatter prevention cover

Claims

1. A rotating electric machine having a rotor including permanent magnets and a rotating shaft, A rotating electric machine housing that rotatably supports the aforementioned rotating shaft, A rotating electric machine system comprising a first bearing and a second bearing interposed between the rotating electric machine housing and the rotating shaft, and arranged at a distance from each other in the axial direction of the rotor, The rotating electric machine housing is provided with a first bearing chamber for housing the first bearing, A first oil nozzle is provided in the first bearing chamber and has a first discharge port for discharging lubricating oil toward the first bearing, An oil circulation supply device that recovers the lubricating oil from the first bearing chamber and supplies it to an oil supply passage provided in the rotating electric machine housing, The system includes an oil splash prevention cover provided within the first bearing chamber and covering the first bearing so as to face the first bearing in the axial direction, The first discharge port is located inside the oil splash prevention cover in a rotating electric machine system.

2. In the rotating electric machine system according to claim 1, The first oil nozzle protrudes from the inner circumferential surface of the oil splash prevention cover in a rotating electric machine system.

3. In the rotating electric machine system according to claim 1, The oil splash prevention cover has a base wall portion facing the first bearing in the axial direction, and a peripheral wall portion protruding in the axial direction from the outer circumference of the base wall portion, in a rotating electric machine system.

4. In the rotating electric machine system according to claim 3, The first oil nozzle is connected to the peripheral wall portion of the rotating electric machine system.

5. In the rotating electric machine system according to claim 1, The oil splash prevention cover has an opening that opens downwards, and is part of a rotating electric machine system.

6. In the rotating electric machine system according to claim 5, A rotating electric machine system wherein the first bearing chamber is provided with an oil discharge port below the opening for discharging the lubricating oil from the first bearing chamber.

7. In the rotating electric machine system according to claim 1, A rotating electric machine system wherein the first bearing chamber is provided with a wall outside the oil splash prevention cover that suppresses the stirring up of the lubricating oil by the airflow generated inside the first bearing chamber.

8. In the rotating electric machine system according to claim 7, The aforementioned wall portion protrudes from the inner circumferential surface of the first bearing chamber, in a rotating electric machine system.

9. In the rotating electric machine system according to claim 1, A rotor channel is formed inside the rotor for circulating the lubricating oil. The rotor has an inlet for the internal flow path of the rotor, The inlet of the rotor internal flow path opens in the first bearing chamber, The first bearing chamber is provided with a second oil nozzle having a second discharge port for discharging the lubricating oil toward the inlet. The second discharge port is located inside the oil splash prevention cover in a rotating electric machine system.

10. In the rotating electric machine system according to any one of claims 1 to 9, The rotating electric machine housing has a gas supply passage for supplying cooling gas into the rotating electric machine housing and a gas discharge passage for discharging the cooling gas from the first bearing chamber. The oil circulation supply device has a tank for recovering the lubricating oil discharged from the rotating electric machine housing via an oil discharge passage and the cooling gas discharged from the rotating electric machine housing via a gas discharge passage, and the lubricating oil recovered by the tank is supplied again to the oil supply passage of the rotating electric machine housing, in a rotating electric machine system.

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