Rotating electric machines

Abstract

Disclosed is a rotary electric machine which is equipped with: a stator which has a teeth section and has a coil wound around the teeth section; a rotor provided coaxially to the stator with a gap interposed therebetween in the radial direction, and having a hollow shaft and a core member which is secured so as to be coaxial to the shaft and around which a field winding is wound; and a coolant channel structure which is connected to a pump for transporting a liquid coolant. Therein, the field winding includes a coil turn section positioned in the axial-direction end section of the rotor, the coolant channel structure includes a first coolant channel which is connected to the interior of the shaft, the first coolant channel extends from the shaft so as to pass more through the inside in the axial direction than through the coil turn section toward the outside in the radial direction, and the first coolant channel has a discharge port which faces the stator in the radial direction and is located in the radially outside end section.

Description

[Technical Field]

[0001] The present disclosure relates to a rotating electric machine. [Background technology]

[0002] As a method for cooling the field winding of a rotating electric machine using a liquid refrigerant such as oil, a technique is known in which the liquid refrigerant is supplied into a hollow rotor shaft, and then supplied to the axial center of the field winding through a radial hole in the rotor shaft (see, for example, Patent Document 1).

[0003] Another known cooling method is to spray a liquid refrigerant from the axial outside onto the axial end of the field winding (the coil turn portion protruding axially from the end face of the rotor core) (see, for example, Patent Document 2). [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Publication No. 2020-39230 [Patent Document 2] International Publication No. 2018 / 095842 Brochure Summary of the Invention [Problem to be solved by the invention]

[0005] However, with the conventional cooling methods described above, it is difficult to effectively cool the stator (especially the coil end portion of the stator coil) in a field winding type rotating electric machine in which the stator is located radially outward of the axial end of the field winding.

[0006] Therefore, an object of the present disclosure is to effectively cool a stator in a field winding type rotating electric machine in which the stator is located radially outward of the axial end portion (coil turn portion) of the field winding. [Means for solving the problem]

[0007] According to one aspect of the present disclosure, a stator includes teeth, and a coil is wound around the teeth; a rotor having a hollow shaft and a core member around which a field winding is wound and which is fixed coaxially to the shaft, the rotor being disposed coaxially with the stator with a gap provided in the radial direction; a refrigerant flow path structure communicating with a pump that pumps the liquid refrigerant; the field winding includes a coil turn portion located at an axial end of the rotor, the refrigerant flow path structure includes a first refrigerant flow path communicating with an interior of the shaft; A rotating electric machine is provided in which the first refrigerant flow path extends radially outward from the shaft, passing axially inward of the coil turn portion, and has an outlet at its radially outer end that is radially opposite the stator. [Effects of the Invention]

[0008] According to the present disclosure, in a field winding type rotating electric machine in which the stator is located radially outward of the axial end of the field winding, the stator can be cooled effectively. [Brief explanation of the drawings]

[0009] [Figure 1] 1 is a skeleton diagram showing an overview of the entire vehicle drive device; [Figure 2] 1 is a schematic cross-sectional view showing an outline of the entire rotating electric machine according to a first embodiment. [Figure 3] 1 is a schematic cross-sectional view showing a part of a cross section of a rotating electric machine; [Figure 4] FIG. 2 is a schematic diagram showing a control system of the rotating electric machine. [Figure 5A] FIG. 3 is an enlarged view of a portion Q1 in FIG. 2. [Figure 5B] FIG. 3 is an enlarged view of part Q3 in FIG. 2. [Figure 5C] FIG. 3 is an enlarged view of part Q2 in FIG. 2. [Figure 6] FIG. 2 is a perspective view showing an example of an end plate. [Figure 7] FIG. 4 is an explanatory diagram of a configuration related to switching of oil passages. [Figure 8] FIG. 10 is a schematic cross-sectional view showing an outline of the entire rotating electric machine according to a second embodiment. [Figure 9] FIG. 9 is an enlarged view of a portion Q4 in FIG. 8. [Figure 10] FIG. 9 is an enlarged view of a portion Q5 in FIG. 8. [Figure 11] 10A and 10B are explanatory diagrams of modified configurations of a pipe section for supplying oil to the hollow interior of the rotor shaft. [Figure 12] FIG. 2 is a perspective view showing an example of an end plate. [Figure 13] FIG. 2 is a perspective view showing an example of an end ring. [Figure 14] FIG. 10 is a schematic cross-sectional view showing an outline of the entire rotating electric machine according to a third embodiment. [Figure 15] FIG. 15 is an enlarged view of part Q6 in FIG. [Figure 16] FIG. 4 is a cross-sectional view showing a part of a spline fitting portion. [Figure 17] FIG. 10 is a cross-sectional view showing a part of a spline fitting portion according to a modified example. [Figure 18] FIG. 10 is a cross-sectional view showing a part of a spline fitting portion according to another modified example. [Figure 19] FIG. 10 is a schematic cross-sectional view showing an outline of the entire rotating electric machine according to another embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0010] Each embodiment will be described in detail below with reference to the accompanying drawings. Note that the dimensional ratios in the drawings are merely examples and are not intended to limit the scope of the invention. In addition, shapes and the like in the drawings may be partially exaggerated for the sake of explanation.

[0011] In the following, first, an overview of the vehicle drive device 100 as a whole will be described, and then the features of this embodiment (first embodiment) will be described in detail.

[0012] Fig. 1 is a skeleton diagram showing an overview of the entire vehicle drive device 100. Fig. 1 defines an X direction and an X1 side and an X2 side along the X direction. The X direction is parallel to the direction of a first axis A1 (hereinafter also referred to as the "axial direction").

[0013] In the example shown in FIG. 1, the vehicle drive device 100 includes a rotating electric machine 1 and a power transmission mechanism 7.

[0014] The rotating electric machine 1 functions as a drive source for the wheels W. In a modified example, an engine (internal combustion engine) may be used as a drive source for the wheels W in addition to the rotating electric machine 1. In this embodiment, the rotating electric machine 1 is a field winding type rotating electric machine, as will be described below, but a permanent magnet may be used in addition to the field winding.

[0015] The power transmission mechanism 7 is provided on a power transmission path connecting the rotating electric machine 1 and the wheels W. The power transmission mechanism 7 includes an input member 3, a counter gear mechanism 4, and a differential gear mechanism 5.

[0016] The input member 3 has an input shaft 31 and an input gear 32. The input shaft 31 is a rotating shaft member that rotates around the first axis A1. The input gear 32 is a gear that transmits rotational torque (driving force) from the rotating electric machine 1 to the counter gear mechanism 4. The input gear 32 is provided on the input shaft 31 of the input member 3 so as to rotate integrally with the input shaft 31 of the input member 3.

[0017] The counter gear mechanism 4 is disposed in the power transmission path between the input member 3 and the differential gear mechanism 5. The counter gear mechanism 4 has a counter shaft 41, a first counter gear 42, and a second counter gear 43.

[0018] The counter shaft 41 is a rotating shaft member that rotates around the second axis A2. The second axis A2 extends parallel to the first axis A1. The first counter gear 42 is an input element of the counter gear mechanism 4. The first counter gear 42 meshes with the input gear 32 of the input member 3. The first counter gear 42 is connected to the counter shaft 41 so as to rotate integrally with the counter shaft 41.

[0019] The second counter gear 43 is an output element of the counter gear mechanism 4. In this embodiment, for example, the second counter gear 43 is formed to have a smaller diameter than the first counter gear 42. The second counter gear 43 is provided on the counter shaft 41 so as to rotate integrally with the counter shaft 41.

[0020] The differential gear mechanism 5 is disposed on a third axis A3, which serves as its rotation axis. The third axis A3 extends parallel to the first axis A1. The differential gear mechanism 5 distributes the driving force transmitted from the rotating electric machine 1 to left and right output members 6A and 6B. The differential gear mechanism 5 includes a differential input gear 51, which meshes with the second counter gear 43 of the counter gear mechanism 4. The differential gear mechanism 5 also includes a differential case 52, which houses a pinion shaft, pinion gears, left and right side gears, etc. The left and right side gears are connected to the left and right output members 6A and 6B so as to rotate integrally with them, respectively.

[0021] The left and right output members 6A, 6B are drivingly connected to the left and right wheels W, respectively. The left and right output members 6A, 6B transmit the driving force distributed by the differential gear mechanism 5 to the wheels W. Note that the left and right output members 6A, 6B may be composed of two or more members.

[0022] In this way, the rotating electric machine 1 drives the wheels W via the power transmission mechanism 7. Details of the power transmission mechanism 7 are arbitrary as long as it includes the rotating electric machine 1. For example, the rotor shaft 314 of the rotating electric machine 1 may be a member that is directly connected to the wheels W. In other embodiments, other power transmission mechanisms such as a planetary gear mechanism may be used, or a power transmission mechanism including a speed-up mechanism may be used.

[0023] FIG. 2 is a schematic cross-sectional view showing an overview of the entire rotating electric machine 1, taken along a plane including the rotation axis of the rotating electric machine 1. FIG. 3 is a schematic cross-sectional view showing a portion of the cross section of the rotating electric machine 1, taken along a plane perpendicular to the rotation axis of the rotating electric machine 1. In FIG. 2, the Z direction and the Z1 side and Z2 side along the Z direction are defined. Here, the Z direction corresponds to the up-down direction, and the Z1 side corresponds to the upper side. Note that the Z direction does not necessarily have to strictly coincide with the vertical direction.

[0024] 2, a part of the case 2 is omitted, and the input shaft 31, the oil supply device 8, the control device 9, and the like are also shown as components of the vehicle drive device 100 other than the rotating electric machine 1. In this embodiment, the input shaft 31 is a solid rotating shaft member as shown in FIG. 2. However, a hollow portion may be formed only in a part of the input shaft 31 (for example, the end portion on the X-side in the X-direction), or a hollow portion for an oil passage may be formed (see the conduit portion 87A in FIG. 11).

[0025] The rotating electric machine 1 includes a rotor 310 and a stator 320 in a case 2 .

[0026] The case 2 may be made of aluminum, for example. The case 2 may be formed by casting, etc. The case 2 may be realized by combining a plurality of case members.

[0027] In this embodiment, the case 2 includes a motor case 250, a first cover member 252, a second cover member 253, and a gear case member 254. As described above, the case 2 houses the rotating electric machine 1 and the power transmission mechanism 7. Furthermore, as schematically shown in FIG. 2, the case 2 may further house a slip ring 318 (described later) and the like.

[0028] The motor case 250 forms a motor housing chamber SP1 that houses the main body of the rotating electric machine 1. The motor case 250 has a peripheral wall that surrounds the radial outside of the rotating electric machine 1. The motor case 250 may be realized by joining multiple members together. Furthermore, the motor case 250 may be integrated with a gear case member 254 on the X1 side in the X direction.

[0029] An internal case oil passage 84 is formed in the motor case 250. In the example shown in Fig. 2, the internal case oil passage 84 extends in the axial direction. The internal case oil passage 84 communicates with an oil pump 80 of the oil supply device 8, which will be described later, and also communicates with oil passage pipes 861 and 862.

[0030] The oil passage pipes 861, 862 are, for example, in the form of hollow pipes (tubes) and extend in the radial direction. The oil passage pipe 861 is disposed on the X1 side of the motor accommodation chamber SP1 in the X direction. One end of the oil passage pipe 861 is connected to the oil passage 84 in the case, and the other end opens at an outlet 8610. The outlet 8610 of the oil passage pipe 861 faces a coil turn portion 3161 (described later) of the field winding 316 from the axially outer side (X1 side in the X direction) in the axial direction. The oil passage pipe 862 is disposed on the X2 side of the motor accommodation chamber SP1 in the X direction. One end of the oil passage pipe 862 is connected to the oil passage 84 in the case, and the other end opens at an outlet 8620. The outlet 8620 of the oil passage pipe 862 faces a coil turn portion 3162 (described later) of the field winding 316 from the axially outer side (X2 side in the X direction) in the axial direction.

[0031] 2, the oil line pipes 861 and 862 are in the form of hollow pipes, but may be formed as part of the in-case oil line 84. For example, part or all of the oil line pipe 861 may be realized by an oil line inside the partition wall portion 2502, which will be described later. Similarly, part or all of the oil line pipe 862 may be realized by an oil line inside the first cover member 252, which will be described later.

[0032] In this embodiment, the motor case 250 has a partition wall 2502 that separates the motor housing chamber SP1 and the gear housing chamber SP2 in the axial direction. Note that the partition wall 2502 does not need to strictly separate the motor housing chamber SP1 and the gear housing chamber SP2, and may be configured to separate them in a manner that allows oil to pass between them, as described below.

[0033] The partition wall portion 2502 has an oil passage 81 for allowing oil to flow. The oil passage 81 is provided above the first axis A1 in the partition wall portion 2502. Specifically, as shown in FIG. 2, the oil passage 81 is disposed above the input shaft 31. One lower end of the oil passage 81 communicates with a space 85 surrounded by the case 2 (partition wall portion 2502) and the bearings 241 and 243, and the other upper end communicates with an oil passage pipe 82 provided in the gear accommodating chamber SP2. The oil passage pipe 82 is in the form of a hollow tube (pipe), one end of which is connected to the oil passage 81, and the other end of which communicates with an oil pump 80 of the oil supply device 8, which will be described later. Note that in the example shown in FIG. 2, the oil passage pipe 82 extends in an oblique direction that becomes increasingly downward as it approaches the X2 side, but the extending direction of the oil passage pipe 82 is arbitrary, and the oil passage pipe 82 may have a bent portion or the like.

[0034] The first cover member 252 is coupled to the X2 side of the motor case 250 in the X direction. The first cover member 252 is in the form of a cover that covers the X2 side of the motor housing chamber SP1 in the X direction. In this case, the first cover member 252 may cover the motor housing chamber SP1 in a manner that completely or almost completely blocks the opening of the motor case 250 on the X2 side in the X direction. Note that a portion of the motor housing chamber SP1 may be formed by the first cover member 252. A bearing 240 that rotatably supports the rotor 310 is provided on the first cover member 252.

[0035] The second cover member 253 is provided on the X2 side in the X direction of the first cover member 252. The second cover member 253 and the first cover member 252 form an accommodation chamber SP3 that accommodates the slip ring 318 of the rotating electric machine 1.

[0036] The gear case member 254 cooperates with the partition wall portion 2502 of the motor case 250 to form a gear accommodating chamber SP2 that accommodates the power transmission mechanism 7. The gear case member 254 cooperates with the partition wall portion 2502 of the motor case 250 to rotatably support the input shaft 31. That is, the input shaft 31 may be rotatably supported by the partition wall portion 2502 of the motor case 250 via the bearing 243 at the end on the X2 side in the X direction, and may be rotatably supported by the gear case member 254 via another bearing (not shown) at the end on the X1 side in the X direction.

[0037] The rotor 310 includes a rotor core 312 , end plates 313 , a rotor shaft 314 , a field winding 316 , end rings 317 , and slip rings 318 .

[0038] Rotor core 312 may be made of, for example, annular laminated steel plates of a magnetic material. As shown in FIG. 3, rotor core 312 has teeth 3122 that protrude radially outward. Conductor wires that form field winding 316 are wound around rotor core 312. Rotor core 312 has an axial through-hole 3120 (see FIG. 2) into which rotor shaft 314 is fitted. Rotor core 312 is fixed to the outer circumferential surface of rotor shaft 314 and rotates integrally with rotor shaft 314.

[0039] End plate 313 is an annular plate that covers the axial end face of rotor core 312. End plate 313 may be coupled to rotor shaft 314 by fitting, for example. End plate 313 is provided on both axial sides of rotor core 312. End plate 313 may have a shape corresponding to the shape of the end face of rotor core 312 when viewed in the axial direction. In other words, end plate 313 may have an outer periphery shaped to correspond to teeth portion 3122, etc. Details of end plate 313 will be described later.

[0040] The rotor shaft 314 defines a first axis A1, which is the rotation axis of the rotating electric machine 1. The rotor shaft 314 is rotatably supported by a first cover member 252 of the case 2 via a bearing 240 on the X2 side in the X direction of a portion to which the rotor core 312 is fixed. The rotor shaft 314 is rotatably supported by a partition wall portion 2502 of the motor case 250 via a bearing 241 on the other axial end side (X1 side in the X direction) of the rotating electric machine 1. In this way, the rotor shaft 314 may be rotatably supported by the case 2 at both axial ends.

[0041] As shown in FIG. 2 and other figures, the rotor shaft 314 is coupled to the input shaft 31 on the X1 side in the X direction so as to be able to transmit power. Specifically, in this embodiment, a spline (hereinafter referred to as a "female spline 71") is formed on the inner peripheral surface of the rotor shaft 314. The rotor shaft 314 is spline-fitted (loose fit) to the input shaft 31 in such a manner that a spline (hereinafter referred to as a "male spline 72") formed on the outer peripheral surface of the input shaft 31 meshes with the female spline 71. Hereinafter, the entire portion where the rotor shaft 314 and the input shaft 31 are coupled by spline fitting in this manner will be referred to as a "spline fitting portion 70."

[0042] The rotor shaft 314 is, for example, in the form of a hollow tube, and has a hollow interior 3145. The hollow interior 3145 may extend over the entire axial length of the rotor shaft 314, but in this embodiment, the X2 side in the X direction is closed (solid). The rotor shaft 314 may be formed from multiple members (pieces).

[0043] The hollow interior 3145 of the rotor shaft 314 functions as the axial oil passage 83. That is, oil is supplied to the hollow interior 3145 via the oil passage 81 of the partition wall portion 2502, as described below. This cools the rotor shaft 314, and thereby the rotor core 312 can be cooled from the radially inner side. As a result, the field winding 316 can also be cooled via the rotor core 312.

[0044] Rotor shaft 314 is formed with radial oil holes 8311 and 8312 for discharging oil to coil turn portions 3161 and 3162 of field winding 316, respectively.

[0045] Oil hole 8311 has an opening that faces radially toward coil turn portion 3161 of field winding 316, and supplies oil from within axial oil passage 83 toward coil turn portion 3161 of field winding 316. Note that, although oil hole 8311 extends linearly parallel to the radial direction in the example shown in Fig. 2, it may also extend linearly in a slightly oblique direction relative to the radial direction.

[0046] Oil hole 8312 has an opening that faces radially toward coil turn portion 3162 of field winding 316, and supplies oil from within axial oil passage 83 toward coil turn portion 3162 of field winding 316. Note that, although oil hole 8312 extends linearly parallel to the radial direction in the example shown in Fig. 2, it may also extend linearly in an oblique direction that is slightly inclined relative to the radial direction.

[0047] 2, the oil holes 8311 and the oil holes 8312 are formed at the same circumferential position around the rotor shaft 314, but they may be formed at different circumferential positions. Also, the oil holes 8311 and the oil holes 8312 may each be provided in multiple positions at different circumferential or axial positions.

[0048] As shown schematically in FIG. 3, the field winding 316 is wound around the teeth 3122 of the rotor core 312. A field current is supplied to the field winding 316, as described below. As shown in FIG. 2, the field winding 316 has coil turn portions 3161 and 3162, which are axial end portions that protrude axially outward from the axial end face of the rotor core 312. The coil turn portion 3161 is located on the X1 side in the X direction, and the coil turn portion 3162 is located on the X2 side in the X direction. That is, the coil turn portion 3161 is located at the axial end portion of the rotor 310 on the X1 side in the X direction, and the coil turn portion 3162 is located at the axial end portion of the rotor 310 on the X2 side in the X direction.

[0049] The end rings 317 are cylindrical and provided on both axial sides. The end ring 317 on the X1 side in the X direction covers the coil turn portion 3161 of the field winding 316 and the end plate 313 from the radially outer side on the X1 side in the X direction. The end ring 317 on the X2 side in the X direction covers the coil turn portion 3162 of the field winding 316 and the end plate 313 from the radially outer side on the X2 side in the X direction. The end rings 317 may be fixed to the end plate 313 by press fitting or the like. The end rings 317 have axial end faces that are approximately perpendicular to the axial direction. The axial end faces of the end rings 317 are preferably flat, but may be inclined to match the shape of the axial end faces of the coil turn portions 3162. Alternatively, the axial end faces of the end rings 317 may have axial irregularities.

[0050] The slip ring 318 is attached to the rotor shaft 314. The slip ring 318 is in the form of a rotary connector, and is provided coaxially with the rotor shaft 314. The slip ring 318 is provided at the end of the rotor shaft 314 on the X2 side. The slip ring 318 includes a conductor ring 3181 and a brush 3182.

[0051] Conductor ring 3181 is provided coaxially with rotor shaft 314 and rotates together with rotor shaft 314. Conductor ring 3181 is electrically connected to field winding 316.

[0052] One end of the brush 3182 is electrically connected in a slidable manner to the conductor ring 3181. The other end of the brush 3182 is electrically connected to the control device 9 and the high-voltage battery 98, which will be described later.

[0053] The stator 320 includes a stator core 321 and a stator coil 322 .

[0054] Stator core 321 may be made of, for example, annular laminated steel plates made of magnetic material. Teeth 3210 protruding radially inward are formed radially on the inner periphery of stator core 321 (only one tooth 3210 is shown in FIG. 3).

[0055] The stator coil 322 may be, for example, a conductor having a rectangular or circular cross section and an insulating coating. The stator coil 322 is wound around the teeth 3210 of the stator core 321, as shown in Fig. 3. Note that the stator coils 322 may be, for example, one or more in parallel and electrically connected in a Y connection or a Delta connection.

[0056] 2, the stator coil 322 has coil end portions 3221 and 3222 that protrude axially outward from the axial end face of the stator core 321. The coil end portion 3221 is located on the X1 side in the X direction, and the coil end portion 3222 is located on the X2 side in the X direction.

[0057] The oil supply device 8 includes an oil pump 80 that pressure-feeds oil (an example of a "liquid refrigerant") to the rotating electric machine 1, etc. The oil pump 80 is supported by the case 2. The oil pump 80 may be disposed arbitrarily, and may be disposed in the motor housing chamber SP1 or the gear housing chamber SP2. The oil pump 80 may be either mechanical or electric. The oil supply device 8 may include a combination of a mechanical oil pump and an electric oil pump. The oil supply device 8 may also include an oil cooler, a strainer, etc. for lowering the temperature of the oil discharged from the oil pump 80.

[0058] The control device 9 is electrically connected to the rotating electric machine 1. The control device 9 controls the rotating electric machine 1. The control device 9 may be disposed, for example, in the accommodation chamber SP3, or may be disposed in a further separate accommodation chamber (not shown).

[0059] 4 is a schematic diagram showing a control system of the rotating electric machine 1. The control device 9 of the rotating electric machine 1 includes a control unit 91 and power conversion circuit sections 92 and 93.

[0060] The control unit 91 may be in the form of an ECU (Electronic Control Unit). The control unit 91 is electrically connected to various electronic components in the vehicle via an appropriate bus such as a CAN (Controller Area Network). The control unit 91 controls the rotating electric machine 1 via power conversion circuit sections 92 and 93 in response to a command relating to a control target value from, for example, an external ECU (not shown). The details of the control method for the rotating electric machine 1 are arbitrary.

[0061] The power conversion circuit unit 92 is, for example, an inverter, and is provided between an on-board high-voltage battery 98 and a stator coil 322 of the rotating electrical machine 1. The power conversion circuit unit 92 supplies three-phase AC current to the stator coil 322 based on the power from the high-voltage battery 98.

[0062] The power conversion circuit unit 93 is, for example, a DC / DC converter, and is provided between an on-board high-voltage battery 98 and the field winding 316 of the rotating electric machine 1. The power conversion circuit unit 93 supplies a field current to the field winding 316 based on the power from the high-voltage battery 98.

[0063] 5A to 6, the manner in which oil is supplied to coil turn portion 3162 of field winding 316 and a preferred configuration of end plate 313 in the oil flow in the oil passage structure of this embodiment will be described.

[0064] The following describes the oil flow when the rotating electric machine 1 is in operation, but flows other than those caused by centrifugal force can also be realized when the rotating electric machine 1 is not in operation. In addition, the following mainly describes the oil flow on the X1 side in the X direction, but the oil flow on the X2 side in the X direction may be substantially the same.

[0065] FIG. 5A is an enlarged view of portion Q1 in FIG. 2. In FIG. 5A, the flow of oil is schematically indicated by arrows R500 to R510. FIG. 5B is an enlarged view of portion Q3 in FIG. 2. In FIG. 5B, the flow of oil is schematically indicated by arrows R500 to R512. FIG. 5C is an enlarged view of portion Q2 in FIG. 2. In FIG. 5C, the flow of oil is schematically indicated by arrows R600 to R604. FIG. 6 is a perspective view showing an example of end plate 313.

[0066] 5A, oil discharged from oil pump 80 passes through oil passage pipe 82 and reaches oil passage 81 in partition wall portion 2502 (see arrow R500). The oil that reaches oil passage 81 flows downward through oil passage 81 (see arrow R502) and drips from opening 810 at the lower end into space portion 85 onto spline fitting portion 70 or its vicinity (see arrow R504). Note that the oil flowing downward through oil passage 81 drips from opening 810 at the lower end due to the influence of gravity, but may also be sprayed from opening 810 at the lower end due to the influence of hydraulic pressure from oil pump 80.

[0067] The oil supplied into space 85 through oil passage 81 in this way accumulates in the lower part of space 85 due to the effect of gravity. This accumulation of oil in space 85 can be promoted by dam members 2411 and 2431 provided on bearings 241 and 243, respectively. Weir member 2411 has the function of blocking oil that may leak from space 85 through bearing 241 into motor housing chamber SP1.

[0068] When the amount of oil pooled in the space 85 becomes relatively large and the upper surface of the oil pool (height of the oil pool) rises above the gap in the spline fitting portion 70 (in Figure 5A, the oil in the space 85 is shown by the hatched area 500), some of the oil pool passes through the gap in the spline fitting portion 70 and reaches the hollow interior 3145 of the rotor shaft 314 (see arrow R506).

[0069] Here, when the rotating electric machine 1 is operating, the rotor shaft 314 is rotating, and the oil that reaches the hollow interior 3145 of the rotor shaft 314 flows along the inner circumferential surface of the rotor shaft 314 due to the action of centrifugal force (see arrow R508). When the oil that flows along the inner circumferential surface of the rotor shaft 314 reaches the inlet (the radially inner opening) of the oil hole 8311, the oil is ejected radially outward from the outlet (the radially outer opening) of the oil hole 8311 (see arrow R510) (see arrow R510). Similarly, when the oil that flows along the inner circumferential surface of the rotor shaft 314 reaches the inlet (the radially inner opening) of the oil hole 8312, the oil is ejected radially outward from the outlet (the radially outer opening) of the oil hole 8312 (not shown) (see arrow R510).

[0070] When the oil in the hollow interior 3145 of the rotor shaft 314 is ejected radially outward by centrifugal force in this manner, the negative pressure in the hollow interior 3145 of the rotor shaft 314 increases. This negative pressure promotes the flow of oil (see arrow R506) through the gaps in the spline fitting portion 70 to the hollow interior 3145 of the rotor shaft 314. Thus, according to this embodiment, by utilizing the negative pressure in the hollow interior 3145 of the rotor shaft 314, the flow of oil (see arrow R506) through the gaps in the spline fitting portion 70 to the hollow interior 3145 of the rotor shaft 314 can be effectively promoted. As a result, even when oil is supplied to the hollow interior 3145 of the rotor shaft 314 through the gaps in the spline fitting portion 70, an appropriate amount of oil can be ensured.

[0071] As shown in FIG. 5C , oil discharged from the oil pump 80 reaches the oil line pipe 861 via the in-case oil passage 84 (see FIG. 2 ) (see arrow R600). The oil that reaches the oil line pipe 861 is ejected from an ejection port 8610 of the oil line pipe 861 toward the axial end face of the end ring 317 (see arrows R602 and R604). Similarly, although not shown, on the X2 side, the oil that reaches the oil line pipe 862 is ejected from an ejection port 8620 of the oil line pipe 862 toward the end ring 317. This allows heat from the coil turn portions 3161 and 3162 to be released via the end ring 317. Note that, to improve this heat release, the end ring 317 is made of a material with high thermal conductivity, such as aluminum. Note that a resin material may be filled between the end ring 317 and the coil turn portion 3161.

[0072] Thus, according to this embodiment, coil turn portions 3161, 3162 of field winding 316 are cooled by oil supplied from hollow interior 3145 of rotor shaft 314. Also, coil turn portions 3161, 3162 of field winding 316 are cooled via oil sprayed from oil line pipes 861, 862 onto end ring 317. This allows coil turn portions 3161, 3162 of field winding 316 to be cooled effectively.

[0073] The outlet 8610 of the oil line pipe 861 (similar to the outlet 8620 of the oil line pipe 862) may face near the radial center (near the center of the radial extension range) of the coil turn portion 3161 of the field winding 316 via the end ring 317, or may face the coil turn portion 3161 radially inward of the radial center.

[0074] 2, in a configuration like this embodiment in which coil turn portions 3161, 3162 of field winding 316 overlap coil end portions 3221, 3222 of stator coil 322 in the axial direction (i.e., a configuration in which the two overlap when viewed radially), the amount of oil supplied to coil end portions 3221, 3222 is likely to decrease. For example, in a configuration like this embodiment in which oil from hollow interior 3145 of rotor shaft 314 is sprayed directly onto coil turn portions 3161, 3162 of field winding 316, oil cannot be sprayed directly onto coil end portions 3221, 3222. For this reason, while such a configuration makes it easy to effectively cool coil turn portions 3161, 3162 of field winding 316, the cooling performance of coil end portions 3221, 3222 by oil from hollow interior 3145 of rotor shaft 314 is likely to decrease.

[0075] In this regard, according to this embodiment, as will be described in detail below, it is possible to ensure the cooling performance of the coil end portions 3221, 3222 by utilizing oil from the hollow interior 3145 of the rotor shaft 314.

[0076] 5B, oil ejected radially outward through oil hole 8311 (see arrow R510 in FIGS. 5A and 5B) passes through oil passage 834 between end plate 313 and rotor core 312, and is supplied (ejected) to coil end portion 3221. This makes it possible to ensure the necessary amount of oil is supplied to coil end portions 3221 and 3222, even in a configuration in which coil turn portions 3161 and 3162 of field winding 316 overlap coil end portions 3221 and 3222 of stator coil 322 in the axial direction.

[0077] 6, end plate 313 has a fitting portion 3132 and a base portion 3133. End plate 313 is preferably made of a material with high thermal conductivity (e.g., aluminum), but may be made of other materials such as resin.

[0078] The fitting portion 3132 has a fitting hole 31320 into which the rotor shaft 314 is fitted.

[0079] The base portion 3133 extends in a plane perpendicular to the axial direction so as to cover the axial end face of the rotor core 312. The base portion 3133 extends radially outward from the outer periphery of the fitting portion 3132.

[0080] A part of the axially inner surface of end plate 313 abuts against the axial end face of rotor core 312 in the axial direction, and oil passage 834 is formed between the remaining part of this surface and rotor core 312. This makes it possible to form oil passage 834 by utilizing end plate 313. Note that field winding 316 is arranged in contact with the axially outer surface of end plate 313.

[0081] The oil passage 834 extends radially outward from the rotor shaft 314, passing axially inward of the coil turn portion 3161. The oil passage 834 has a discharge port 8343 at its radially outer end. The discharge port 8343 faces the stator 320 in the radial direction. In this embodiment, the discharge port 8343 faces the coil end portion 3221 of the stator coil 322 in the radial direction.

[0082] Specifically, the oil passage 834 includes, as oil passage portions, a first flow passage portion 8341 extending in an annular shape and a plurality of second flow passage portions 8342.

[0083] The first flow path portion 8341 is formed radially inside the base portion 3133. The first flow path portion 8341 faces the rotor shaft 314 in the radial direction and is continuous with the oil hole portion 8311 of the rotor shaft 314. By providing the first flow path portion 8341 extending in an annular shape, oil can be distributed to a plurality of second flow path portions 8342, which will be described later.

[0084] The second flow path portion 8342 extends radially outward from the first flow path portion 8341. The second flow path portion 8342 may be formed in each of the radial portions of the base portion 3133. The radially outer end of the second flow path portion 8342 communicates with the discharge port 8343.

[0085] 5B, oil in rotor shaft 314 is introduced into first flow path portion 8341 of oil passage 834 via oil hole portion 8311 due to the influence of centrifugal force (see arrow R510). Then, the oil introduced into first flow path portion 8341 is further caused by the influence of centrifugal force to flow radially outward through second flow path portion 8342 and is ejected from discharge port 8343 to coil end portion 3221 (see arrow R512). This effectively cools coil end portion 3221.

[0086] In particular, according to this embodiment, the oil inside rotor shaft 314 is not sprayed directly onto field winding 316, but is sprayed onto coil end portion 3221 via oil passage 834. This makes it possible to supply oil with a higher cooling capacity (i.e., low-temperature oil) to coil end portion 3221 than when oil that has passed through field winding 316 is supplied to coil end portion 3221, thereby increasing the cooling capacity for coil end portion 3221.

[0087] Furthermore, according to this embodiment, since the oil passage 834 is provided on the axially inner side of the end plate 313, oil can be easily guided to the coil end portion 3221 via the oil passage 834 even when the coil end portion 3221 is positioned axially inner than the coil turn portion 3161.

[0088] In the present embodiment, the circumferential position of the oil hole 8311 may coincide with the circumferential position of at least one of the plurality of second flow path portions 8342. In this case, the oil ejected radially outward from the oil hole 8311 is relatively easily supplied to the second flow path portion 8342 that is radially opposed to the oil hole 8311. This allows oil to be efficiently supplied to the coil end portion 3221.

[0089] However, when the circumferential positions of one or more oil holes 8311 coincide with the circumferential positions of several second flow path portions 8342, it becomes difficult for oil to be supplied to the other second flow path portions 8342 that do not coincide with the circumferential position of the oil hole 8311. Therefore, in order to equalize the amount of oil flowing through each second flow path portion 8342, all of the oil holes 8311 may be offset circumferentially with respect to the multiple second flow path portions 8342. In other words, the circumferential positions of the oil holes 8311 and the second flow path portions 8342 may be set so that there is not even one second flow path portion 8342 that coincides with the circumferential position of an oil hole 8311.

[0090] Next, a configuration relating to switching of oil passages will be described with reference to FIG.

[0091] FIG. 7 is an explanatory diagram of a configuration related to oil passage switching. In the example shown in FIG. 7, a valve 88 is provided that switches the flow path of oil discharged from an oil pump 80 to an oil passage pipe 82 or an in-case oil passage 84. The valve 88 may be, for example, an electronically controllable electromagnetic valve. The valve 88 may be provided, for example, at point P1 shown in FIG. 2. The valve 88 is controlled by a control device 9A. The control device 9A may be realized by the same control unit as the control device 9 described above.

[0092] Information for calculating and acquiring the value of the switching parameter may be input to the control device 9A (see R800). When a preset switching condition is satisfied based on the value of the switching parameter, the control device 9A sends a command to the valve 88 (see R802), thereby switching the state of the valve 88 between a first state in which oil from the oil pump 80 is supplied to the oil line pipe 82, and a second state in which oil from the oil pump 80 is supplied to the in-case oil line 84.

[0093] In the first state, oil from the oil pump 80 is supplied into the rotor shaft 314 via the oil line 82, as described above, and then supplied to the coil turn portions 3161, 3162 of the field winding 316 and then to the coil end portions 3221, 3222 of the stator coil 322.

[0094] In the second state, oil from the oil pump 80 is used to cool the coil turn portions 3161, 3162 of the field winding 316 and the coil end portions 3221, 3222 of the stator coil 322 via the internal oil passage 84 and the oil passage pipes 861, 862, as described above.

[0095] The switching parameter is arbitrary and may be, for example, the rotational speed of the rotating electric machine 1. In this case, the condition for switching to the second state may be satisfied when the rotational speed of the rotating electric machine 1 is equal to or less than a relatively low first threshold value Th1. The first threshold value Th1 is arbitrary and may correspond to the lower limit of a speed range in which the air flow around the coil turn portions 3161, 3162 described above does not significantly impede the ejection of oil from the oil line pipes 861, 862. Furthermore, the condition for switching to the first state may be satisfied when the rotational speed of the rotating electric machine 1 is equal to or greater than a relatively high second threshold value Th2. The second threshold value Th2 is arbitrary and may be a rotational speed at which the negative pressure described above becomes relatively high.

[0096] 7 is a configuration in which the valve 88 is used to selectively switch between the first state and the second state, but the present invention is not limited to this. For example, a valve that can vary the distribution ratio, such as a flow rate adjustment valve, may be provided instead of the valve 88. In this case, the distribution ratio may be controlled so that the amount (proportion) of oil that is supplied to the oil line pipe 82 (and thereafter into the rotor shaft 314) of the oil discharged from the oil pump 80 increases as the rotational speed of the rotary electric machine 1 increases (see R802).

[0097] 7, the oil pump 80 may be electrically driven. In this case, the control device 9A may control the oil pump 80 in the second state so that the discharge amount of the oil pump 80 increases as the rotation speed of the rotating electric machine 1 increases (see R804).

[0098] Alternatively, oil pump 80 may be controlled in accordance with the magnitude of the field current applied to field winding 316, power, etc. In this case, for example, oil pump 80 may be controlled so that the discharge rate of oil pump 80 increases as the magnitude of the field current applied to field winding 316 increases. Alternatively, if a temperature sensor (e.g., a thermistor) is provided in field winding 316, oil pump 80 may be controlled so that the discharge rate of oil pump 80 increases as the temperature of field winding 316 increases.

[0099] Next, another embodiment (embodiment 2) will be described with reference to FIGS.

[0100] The vehicle drive device 100A according to this embodiment differs from the vehicle drive device 100 according to the above-described embodiment (embodiment 1) mainly in the oil passage structure, and the following mainly describes components related to the oil passage structure. In the following embodiments, components similar to those in embodiment 1 described above will be assigned the same reference numerals and descriptions thereof will be omitted.

[0101] FIG. 8 is a schematic cross-sectional view showing an outline of the entire rotating electrical machine 1A according to the second embodiment.

[0102] The rotor 310 includes a rotor core 312 , an end plate 313A, a rotor shaft 314 , a field winding 316 , an end ring 317A, and a slip ring 318 .

[0103] The field winding 316 may be the same as that in the first embodiment, but in this embodiment, varnish or the like may be applied to portions that come into contact with oil, which will be described later.

[0104] End plate 313A is an annular plate that covers the axial end face of rotor core 312. End plate 313A may be coupled to rotor shaft 314 by fitting, for example. End plate 313A is provided on both axial sides of rotor core 312. End plate 313A may have a shape corresponding to the shape of the end face of rotor core 312 when viewed in the axial direction. In other words, end plate 313A may have an outer periphery shaped to correspond to teeth portion 3122, etc. Details of end plate 313A will be described later.

[0105] The end rings 317A are cylindrical and provided on both axial sides. The end ring 317A on the X1 side in the X direction covers the coil turn portion 3161 of the field winding 316 and the end plate 313A from the radially outer side on the X1 side in the X direction. The end ring 317A on the X2 side in the X direction covers the coil turn portion 3162 of the field winding 316 and the end plate 313A from the radially outer side on the X2 side in the X direction. The end ring 317A may be fixed to the end plate 313A by press fitting or the like. Details of the end ring 317A will be described later.

[0106] 9 to 13, the oil flow in the oil passage structure of this embodiment, including the supply of oil to coil turn portion 3162 of field winding 316 and preferred configurations of end plate 313A and end ring 317A, will be described.

[0107] The following describes the oil flow when the rotating electric machine 1 is in operation, but flows other than those caused by centrifugal force can also be realized when the rotating electric machine 1 is not in operation. In addition, the following mainly describes the oil flow on the X1 side in the X direction, but the oil flow on the X2 side in the X direction may be substantially the same.

[0108] Fig. 9 is an enlarged view of part Q4 in Fig. 8. In Fig. 9, the flow of oil is schematically indicated by arrows R500 to R510. Fig. 10 is an enlarged view of part Q5 in Fig. 8. In Fig. 10, the flow of oil is typically indicated by arrows R600 to R610. Fig. 12 is a perspective view showing an example of end plate 313A, and Fig. 13 is a perspective view showing an example of end ring 317A.

[0109] 9, oil discharged from oil pump 80 passes through oil passage pipe 82 and reaches oil passage 81 in partition wall portion 2502 (see arrow R500). The oil that reaches oil passage 81 flows downward through oil passage 81 (see arrow R502) and drips from opening 810 at the lower end into space portion 85 onto spline fitting portion 70 or its vicinity (see arrow R504). Note that the oil flowing downward through oil passage 81 drips from opening 810 at the lower end due to the influence of gravity, but may also be sprayed from opening 810 at the lower end due to the influence of hydraulic pressure from oil pump 80.

[0110] The oil supplied into space 85 through oil passage 81 in this way accumulates in the lower part of space 85 due to the effect of gravity. This accumulation of oil in space 85 can be promoted by dam members 2411 and 2431 provided on bearings 241 and 243, respectively. Weir member 2411 has the function of blocking oil that may leak from space 85 through bearing 241 into motor housing chamber SP1.

[0111] When the amount of oil pooled in the space 85 becomes relatively large and the upper surface of the oil pool (height of the oil pool) rises above the gap in the spline fitting portion 70 (in Figure 9, the oil in the space 85 is shown by the hatched area 500), some of the oil pool passes through the gap in the spline fitting portion 70 and reaches the hollow interior 3145 of the rotor shaft 314 (see arrow R506).

[0112] Here, when the rotating electric machine 1 is operating, the rotor shaft 314 is rotating, and the oil that reaches the hollow interior 3145 of the rotor shaft 314 flows along the inner circumferential surface of the rotor shaft 314 due to the action of centrifugal force (see arrow R508). When the oil that flows along the inner circumferential surface of the rotor shaft 314 reaches the inlet (the radially inner opening) of the oil hole 8311A, the oil is sprayed out radially outward from the outlet (the radially outer opening) of the oil hole 8311A towards the coil turn portion 3161 of the field winding 316 due to the action of centrifugal force (see arrow R510). Similarly, when the flow along the inner circumferential surface of rotor shaft 314 reaches the inlet (radially inner opening) of oil hole portion 8312A, centrifugal force causes it to be ejected radially outward from the outlet (radially outer opening) of oil hole portion 8312A toward coil turn portion 3162 of field winding 316 (not shown).

[0113] When the oil in the hollow interior 3145 of the rotor shaft 314 is ejected radially outward by centrifugal force in this manner, the negative pressure in the hollow interior 3145 of the rotor shaft 314 increases. This negative pressure promotes the flow of oil (see arrow R506) through the gaps in the spline fitting portion 70 to the hollow interior 3145 of the rotor shaft 314. Thus, according to this embodiment, by utilizing the negative pressure in the hollow interior 3145 of the rotor shaft 314, the flow of oil (see arrow R506) through the gaps in the spline fitting portion 70 to the hollow interior 3145 of the rotor shaft 314 can be effectively promoted. As a result, even when oil is supplied to the hollow interior 3145 of the rotor shaft 314 through the gaps in the spline fitting portion 70, an appropriate amount of oil can be ensured.

[0114] 10, oil discharged from oil pump 80 reaches oil line pipe 861A via in-case oil passage 84 (see arrow R600). The oil that has reached oil line pipe 861A is sprayed from a discharge port 8610A of oil line pipe 861A onto coil turn portion 3161 of field winding 316 (see arrow R604). Similarly, although not shown, the oil that reaches oil line pipe 862A is sprayed from a discharge port 8620A of oil line pipe 862A onto coil turn portion 3162 of field winding 316.

[0115] Thus, according to this embodiment, oil is ejected from the radially inner side from hollow interior 3145 of rotor shaft 314, and oil is ejected from the axially outer side from oil passage pipes 861A and 862A onto coil turn portions 3161 and 3162 of field winding 316. This allows coil turn portions 3161 and 3162 of field winding 316 to be cooled effectively.

[0116] The outlet 8610A of the oil line pipe 861A (and the outlet 8620A of the oil line pipe 862A) may face near the radial center of the coil turn portion 3161 of the field winding 316, or may face the coil turn portion 3161 radially inward from the radial center. In this case, it can be expected that the oil will be distributed over the entire radial direction of the coil turn portion 3161 of the field winding 316 due to the action of centrifugal force. Alternatively, the outlet 8610A of the oil line pipe 861A (and the outlet 8620A of the oil line pipe 862A) may face the coil turn portion 3161 radially outward and vertically above the radial center of the coil turn portion 3161 of the field winding 316. In this case, it can be expected that the oil will be distributed over the entire radial direction of the coil turn portion 3161 of the field winding 316 due to the effect of gravity.

[0117] In this embodiment, as in the above-described embodiments, oil is also supplied from the hollow interior 3145 of the rotor shaft 314 to the coil turn portions 3161, 3162 of the field winding 316 from the radially inner side, so that even when the rotor 310 is rotating at high speed, the coil turn portions 3161, 3162 can be effectively cooled by the oil from the hollow interior 3145 of the rotor shaft 314.

[0118] Furthermore, according to this embodiment, when rotor 310 is rotating at low speeds, which tends to reduce the amount of oil supplied to hollow interior 3145 of rotor shaft 314 due to the decrease in negative pressure described above, a relatively large amount of oil can be applied to coil turn portions 3161, 3162 of field winding 316 via oil line pipes 861A, 862A.

[0119] In this way, this embodiment also makes it easy to stabilize the amount of oil supplied to the coil turn portions 3161, 3162 over the entire range of possible rotational speeds of the rotor 310. In this regard, as will be described later with reference to FIG. 7, it is also possible to switch the oil passages depending on the rotational speed of the rotor 310.

[0120] In this embodiment, as shown in FIGS. 8 and 9 , oil is supplied to the hollow interior 3145 of the rotor shaft 314 through a conduit portion formed by a combination of the oil passage 81 and the oil conduit pipe 82, and through the space 85 and the gap between the female spline 71. However, the configuration of the conduit portion for supplying oil to the hollow interior 3145 of the rotor shaft 314 may be various and is not limited to this. For example, as shown in FIG. 11 , the oil passage 81 and the oil conduit pipe 82 may be replaced with a conduit portion 81A formed in the partition wall portion 2502A. In this case, the radially outer end of the conduit portion 81A may be connected to the in-case oil passage 84 (see FIG. 8 ). This conduit portion 81A can also supply oil to the rotor shaft 314 in a similar manner through the above-described space 85 and the like (see arrow R504A). Alternatively, as shown in FIG. 11 , the oil passage 81 and the oil conduit pipe 82 may be replaced with a conduit portion 87A inside the hollow input shaft 31A. In this case, the end of the pipe line portion 87A on the X2 side in the X direction may be directly connected to the hollow interior 3145 of the rotor shaft 314, and the end on the X1 side in the X direction may be connected to the oil pump 80. Oil can be supplied to the inside of the rotor shaft 314 by the pipe line portion 87A (see arrow R505A). In this case, the hollow input shaft 31A is one component of the rotating electric machine 1 as an example of a second refrigerant pipe portion. In another modified example, oil may be supplied to the inside of the rotor shaft 314 from the X2 side in the X direction by a pipe line portion (not shown). Such a modified example is also applicable to the above-described first embodiment.

[0121] 8 , in a configuration like this embodiment in which coil turn portions 3161, 3162 of field winding 316 overlap coil end portions 3221, 3222 of stator coil 322 in the axial direction (i.e., a configuration in which the two overlap when viewed radially), the amount of oil supplied to coil end portions 3221, 3222 is likely to decrease. For example, in a configuration like this embodiment in which oil from hollow interior 3145 of rotor shaft 314 is sprayed directly onto coil turn portions 3161, 3162 of field winding 316, oil cannot be sprayed directly onto coil end portions 3221, 3222. Therefore, in this configuration, while coil turn portions 3161, 3162 of field winding 316 can be effectively cooled, the cooling performance of coil end portions 3221, 3222 by oil from hollow interior 3145 of rotor shaft 314 is likely to decrease.

[0122] In this regard, according to the present embodiment, as will be described in detail below, a configuration is adopted in which oil from the hollow interior 3145 of the rotor shaft 314 is sprayed directly onto the coil turn portions 3161, 3162 of the field winding 316, while ensuring the cooling performance of the coil end portions 3221, 3222.

[0123] 9 and 10, oil injected into the coil turn portion 3161 through the oil hole 8311A (see arrow R510 in FIGS. 9 and 10) and oil injected into the coil turn portion 3161 through the oil passage pipe 861A (see arrow R604 in FIG. 10) are supplied to the coil end portion 3221 through the oil passage 89 relating to the gap between the coil turn portion 3161 or the end plate 313A and the end ring 317A. This makes it possible to ensure the necessary amount of oil is supplied to the coil end portions 3221 and 3222, even in a configuration in which the coil turn portions 3161 and 3162 of the field winding 316 overlap with the coil end portions 3221 and 3222 of the stator coil 322 in the axial direction.

[0124] Specifically, in this embodiment, the end plate 313A has a fitting portion 3132A, a base portion 3133A, and a wall portion 3134, as shown in FIG.

[0125] The fitting portion 3132A has a fitting hole 31320 into which the rotor shaft 314 is fitted.

[0126] Base portion 3133A extends in a plane perpendicular to the axial direction so as to cover the axial end face of rotor core 312. Base portion 3133A extends radially outward in the radial direction from the outer periphery of fitting portion 3132A.

[0127] The wall portion 3134 is provided at the radially outer end of the base portion 3133A. The wall portion 3134 is erected in the axial direction in a manner facing the coil turn portion 3161 from the radially outer side. A groove portion 31342 is provided on the radially outer side of the wall portion 3134. As shown in FIG. 12, the groove portion 31342 may extend in the axial direction. In the example shown in FIG. 12, two groove portions 31342 are formed for each wall portion 3134, but the number of groove portions 31342 is arbitrary.

[0128] In this embodiment, the end ring 317A has a peripheral wall portion 3170 and an annular wall portion 3172, as shown in FIGS.

[0129] The peripheral wall portion 3170 extends in the circumferential and axial directions radially outside the coil turn portion 3161. The peripheral wall portion 3170 faces the wall portion 3134 of the end plate 313A from the radially outside in the radial direction. The peripheral wall portion 3170 may be fixed to the wall portion 3134 by press-fitting. The peripheral wall portion 3170 is disposed radially inside the coil end portion 3221 and faces the coil end portion 3221 in the radial direction. The peripheral wall portion 3170 has a radial hole 31702, and the hole 31702 faces the coil end portion 3221 in the radial direction. That is, the peripheral wall portion 3170 has the hole 31702 at a position radially facing the coil end portion 3221. Oil in an oil passage 890 (described later) is sprayed from the hole 31702 toward the coil end portion 3221 (see arrow R610 in FIG. 10 ).

[0130] 13, a plurality of holes 31702 (in this example, as an example, four holes 31702 corresponding to the four wall portions 3134) may be formed along the circumferential direction in a manner to face radially on the wall portion 3134 of the end plate 313A, and / or a plurality of holes 31702 may be formed along the axial direction. Also, instead of the holes 31702, an axial gap between the peripheral wall portion 3170 and the outer peripheral edge portion of the end plate 313A may be made to function in the same way as the holes 31702.

[0131] The peripheral wall portion 3170 is positioned relative to the wall portion 3134 of the end plate 313A in such a manner that a radial gap is formed between the peripheral wall portion 3170 and the wall portion 3134. In this case, an oil passage 890 formed by the radial gap between the peripheral wall portion 3170 and the wall portion 3134 can be formed as part of the oil passage 89. One end of the oil passage 890 communicates with an oil passage 891, which will be described later, and the other end communicates with a hole 31702 of the end ring 317A.

[0132] In the present embodiment, oil passage 890 formed by a gap between peripheral wall portion 3170 and wall portion 3134 in the radial direction is formed by axial groove portion 31342 in wall portion 3134. This allows oil in oil passage 890 to flow more easily in the axial direction, thereby reducing circumferential leakage of oil in oil passage 890 (leakage from the circumferential edge portion of wall portion 3134). Note that in a modified example, oil passage 890 may be realized by a groove portion (extending in the axial direction) similarly formed on the peripheral wall portion 3170 side, instead of groove portion 31342 in wall portion 3134. Furthermore, in the present embodiment, oil passage 890 extends linearly in the axial direction in a portion of the circumferential direction of wall portion 3134, but may also extend linearly in the axial direction over the entire circumferential direction of wall portion 3134.

[0133] The annular wall portion 3172 extends radially inward from the axial end of the peripheral wall portion 3170. The annular wall portion 3172 also faces the base portion 3133A in the axial direction from the axially outer side. This allows oil that may flow axially and radially outward from the coil turn portion 3161 to be guided to the oil passage 89, thereby enabling oil to be efficiently supplied to the coil end portion 3221.

[0134] 10 , the annular wall portion 3172 is preferably disposed axially outward of or at the same axial position as the ejection port 8610A of the oil line pipe 861A. In other words, the ejection port 8610A of the oil line pipe 861A is located radially inward of the annular wall portion 3172 and is disposed so as to overlap with the annular wall portion 3172 as viewed in the radial direction, or is disposed so as to be closer to the coil turn portion 3161 in the axial direction than the annular wall portion 3172. This effectively reduces the possibility that oil ejected from the ejection port 8610A of the oil line pipe 861A will be scattered axially outward of the annular wall portion 3172 due to air flow around the coil turn portion 3161, splashing, or the like. However, in a modified example, the outlet 8610A of the oil passage pipe 861A may be located radially inward of the annular wall portion 3172 and may be located axially farther from the coil turn portion 3161 than the annular wall portion 3172.

[0135] Furthermore, the annular wall portion 3172 preferably faces the coil turn portion 3161 in the axial direction from the axially outer side. That is, the annular wall portion 3172 is spaced apart from the coil turn portion 3161 in the axial direction, and overlaps with the coil turn portion 3161 as viewed in the axial direction. In this case, an oil passage 891 formed by a gap between the annular wall portion 3172 and the coil turn portion 3161 can be formed as part of the oil passage 89, and oil can be efficiently supplied to the coil end portion 3221 (see arrow R608 in FIG. 10 ).

[0136] Thus, according to this embodiment, as described above, the oil ejected from the radially inner side and the axially outer side toward the coil turn portion 3161 hits the coil turn portion 3161 (see arrows R510 and R604 in FIG. 10), cools the coil turn portion 3161, and is then directed radially outward by centrifugal force or the like (see arrow R606 in FIG. 10). The oil directed radially outward can be guided to the coil end portion 3221 via the oil passage 89, enabling the coil end portion 3221 to be efficiently cooled.

[0137] In particular, according to this embodiment, as described above, the oil passage 89 includes the oil passage 890 formed by the gap between the peripheral wall portion 3170 and the wall portion 3134 in the radial direction, and the oil passage 891 formed by the gap between the annular wall portion 3172 and the coil turn portion 3161. This makes it possible to efficiently collect oil sprayed toward the coil turn portion 3161 and guide it to the coil end portion 3221 (see arrows R606 to R610 in FIG. 10 ). In other words, it is possible to maximize the proportion of oil that can be guided to the coil end portion 3221 out of the oil sprayed toward the coil turn portion 3161 from the radial inside and the axial outside. This makes it possible to effectively cool not only the coil turn portion 3161 but also the coil end portion 3221.

[0138] Furthermore, according to this embodiment, even when the coil end portion 3221 is located axially more inward than the coil turn portion 3161, the oil can be guided axially more inward via the oil passage 890 (see arrow R609 in FIG. 10), thereby realizing cooling of the coil end portion 3221 by the oil sprayed toward the coil turn portion 3161. Note that if the coil end portion 3221 is not located axially more inward than the coil turn portion 3161 (for example, if they are at approximately the same axial position), the oil passage 890 may be omitted.

[0139] The above-described second embodiment can be realized by appropriately combining it with the above-described first embodiment. For example, in the above-described first embodiment, the end ring 317A according to the second embodiment may be replaced with the end ring 317 according to the above-described first embodiment.

[0140] Next, another embodiment (Embodiment 3) will be described with reference to Figures 14 to 18. The vehicle drive device 100B according to this embodiment differs from the vehicle drive device 100 according to the embodiment (Embodiment 1) described above mainly in terms of the oil passage structure, and the following description will mainly focus on components related to the oil passage structure. In the following embodiment, components similar to those in the embodiment 1 described above will be assigned the same reference numerals and will not be described again.

[0141] FIG. 14 is a schematic cross-sectional view showing an outline of the entire rotating electrical machine 1B according to the third embodiment.

[0142] The rotating electric machine 1B according to this embodiment has an oil passage structure that is different from that of the rotating electric machine 1 according to the first embodiment described above. Below, with reference to Figures 15 to 18, the flow of oil in the oil passage structure of this embodiment will be described, mainly focusing on the manner in which oil is supplied via the spline fitting portion 70. Note that, although the flow of oil when the rotating electric machine 1B is driven will be described below, flows other than those caused by centrifugal force can also be realized when the rotating electric machine 1B is not driven.

[0143] Fig. 15 is an enlarged view of part Q6 in Fig. 14. In Fig. 15, the flow of oil is schematically shown by arrows R500 to R510. Fig. 16 is a cross-sectional view showing a part of the spline fitting portion 70. Fig. 17 is a cross-sectional view showing a part of a spline fitting portion 70A according to one modified example.

[0144] Oil discharged from oil pump 80 passes through oil passage pipe 82 and reaches oil passage 81 in partition wall portion 2502 (see arrow R500). The oil that reaches oil passage 81 flows downward through oil passage 81 (see arrow R502) and drips from opening 810 at the lower end into space portion 85 onto spline fitting portion 70 or its vicinity (see arrow R504). The vicinity of spline fitting portion 70 is a concept that includes a range on the X1 side of spline fitting portion 70 and on the X2 side of bearing 243. Note that the oil flowing downward through oil passage 81 drips from opening 810 at the lower end due to the effect of gravity, but may also be sprayed from opening 810 at the lower end due to the effect of hydraulic pressure from oil pump 80.

[0145] The oil supplied into the space 85 through the oil passage 81 in this manner accumulates in the lower part of the space 85 due to the effect of gravity. This accumulation of oil in the space 85 can be promoted by dam members 2411 and 2431 provided in the bearings 241 and 243, respectively. The dam member 2411 functions to block oil that may leak from the space 85 through the bearing 241 into the motor housing chamber SP1. As schematically shown in FIG. 14 , the dam member 2411 is provided to cover the gap between the inner race and the outer race of the bearing 241. The dam member 2411 does not need to be provided around the entire circumference of the bearing 241, but may be provided in a circumferential section on the lower side. The dam member 2431 functions to block oil that may leak from the space 85 through the bearing 243 into the gear housing chamber SP2. 14, the dam member 2431 is provided so as to cover the gap between the inner race and the outer race of the bearing 243. The dam member 2431 does not need to be provided around the entire circumference of the bearing 243, and may be provided in a circumferential section on the lower side.

[0146] When the amount of oil pooled in the space 85 becomes relatively large and the upper surface of the oil pool (height of the oil pool) rises above the gap S70 (see FIG. 16) of the spline fitting portion 70 (in FIG. 15, the oil in the space 85 is shown by a hatched area 500), part of the oil pool passes through the gap S70 of the spline fitting portion 70 and reaches the hollow interior 3145 of the rotor shaft 314 (see arrow R506). Note that, depending on the state of oil supply to the space 85, there may be cases where the upper surface of the oil pool remains above the gap S70 of the spline fitting portion 70, in which case part of the oil pool continues to pass through the gap S70 of the spline fitting portion 70 and reaches the hollow interior 3145 of the rotor shaft 314.

[0147] In the example shown in Fig. 16, the meshing of the female spline 71 and the male spline 72 in the spline fitting portion 70 is achieved by large diameter fitting, in which the tooth tip (large diameter surface 721) of the male spline 72 abuts against the tooth base (large diameter surface 711) of the female spline 71 in the radial direction. In this case, the gap S70 of the spline fitting portion 70 may include a gap S71 between the teeth in the circumferential direction, and a gap S72 between the tooth base of the male spline 72 and the tooth tip of the female spline 71 in the radial direction. Note that Fig. 16 schematically shows a line L700, which indicates an example of the upper surface of the oil pool (height of the oil pool) when it exceeds the gap S72, by a two-dot chain line.

[0148] 17, the engagement of the female splines 71A and the male splines 72A at the spline engagement portion 70A between the input shaft 31 and the rotor shaft 314A is achieved by tooth flank alignment. In this case, the gap S70A at the spline engagement portion 70A may include a gap S73A between the tip (large diameter surface 721A) of the male spline 72A and the root (large diameter surface 711A) of the female spline 71A in the radial direction, and a gap S74A between the root (large diameter surface 711A) of the male spline 72A and the tip (large diameter surface 711A) of the female spline 71A in the radial direction. In addition, in FIG. 17, a line L702 showing an example of the upper surface of the oil reservoir (height of the oil reservoir) significantly exceeding the gap S73A is schematically shown by a two-dot chain line.

[0149] Here, when rotating electric machine 1B is operating, rotor shaft 314 is rotating, and oil reaching hollow interior 3145 of rotor shaft 314 flows along the inner circumferential surface of rotor shaft 314 due to the action of centrifugal force (see arrow R508). When the oil flowing along the inner circumferential surface of rotor shaft 314 reaches the inlet (radially inner opening) of oil hole 8311B, centrifugal force causes the oil to be ejected radially outward from the outlet (radially outer opening) of oil hole 8311B toward coil turn portion 3161 of field winding 316 (see arrow R510). Similarly, when the flow along the inner circumferential surface of rotor shaft 314 reaches the inlet (radially inner opening) of oil hole portion 8312B, centrifugal force causes it to be ejected radially outward from the outlet (radially outer opening) of oil hole portion 8312B toward coil turn portion 3162 of field winding 316 (not shown).

[0150] When the oil in the hollow interior 3145 of the rotor shaft 314 is ejected radially outward by centrifugal force in this manner, the negative pressure in the hollow interior 3145 of the rotor shaft 314 increases. This negative pressure promotes the flow of oil (see arrow R506) through the gap S70 of the spline fitting portion 70 to the hollow interior 3145 of the rotor shaft 314. Thus, according to this embodiment, by utilizing the negative pressure in the hollow interior 3145 of the rotor shaft 314, the flow of oil (see arrow R506) through the gap S70 of the spline fitting portion 70 to the hollow interior 3145 of the rotor shaft 314 can be effectively promoted. As a result, even when oil is supplied to the hollow interior 3145 of the rotor shaft 314 through the gap S70 of the spline fitting portion 70, an appropriate amount of oil can be ensured.

[0151] In particular, the negative pressure in hollow interior 3145 of rotor shaft 314 increases as the rotation speed of rotor shaft 314 (i.e., the rotation speed of rotating electric machine 1B) increases. Therefore, during high-speed rotation, when the temperature of field winding 316 is likely to become relatively high, a relatively large amount of oil can be applied to field winding 316.

[0152] Furthermore, according to this embodiment, the hollow interior 3145 of the rotor shaft 314 is closed on the X2 side in the X direction as described above, so negative pressure is more likely to increase than when the X2 side in the X direction is open. This effectively promotes the flow of oil (see arrow R506) through the gap S70 of the spline fitting portion 70 to the hollow interior 3145 of the rotor shaft 314.

[0153] In this manner, according to the present embodiment, oil can be supplied from the X1 side of the rotor shaft 314 in the X direction to the hollow interior 3145 of the rotor shaft 314 via the space 85 and the spline fitting portion 70. This simplifies or eliminates the oil passage structure on the X2 side of the rotor shaft 314 in the X direction. As a result, compared to the conventional technology (see, for example, Patent Document 1) in which oil is supplied from the X2 side of the rotor shaft 314 in the X direction (the side not connected to the rotating electric machine 1B), it is possible to save space on the X2 side of the rotor shaft 314 in the X direction or increase the flexibility of use for other applications. In other words, according to the present embodiment, in a vehicle drive device 100B including the rotating electric machine 1B and the power transmission mechanism 7, it is possible to save space on the side not connected to the rotating electric machine 1B or increase the flexibility of arrangement of other members.

[0154] Here, in this embodiment, slip ring 318 is provided on the X2 side of rotor shaft 314 in the X direction (the side not connected to rotating electric machine 1B). In this embodiment, there is no complex oil passage structure on the X2 side of rotor shaft 314 in the X direction, so it is easy to ensure space for arranging slip ring 318 on the X2 side of rotor shaft 314 in the X direction. In particular, slip ring 318 needs to be highly waterproof (for example, completely waterproof), which may require a relatively large installation space, but in this embodiment, it is easy to ensure such a relatively large installation space.

[0155] Furthermore, according to this embodiment, oil is supplied to the hollow interior 3145 of the rotor shaft 314 through the gap S70 of the spline fitting portion 70, thereby achieving oil lubrication of the spline fitting portion 70. In other words, oil can be stably supplied as lubricating oil to the spline fitting portion 70, which is a power transmission portion, and the reliability (for example, wear resistance, etc.) of the spline fitting portion 70 can be improved.

[0156] Furthermore, according to this embodiment, oil is supplied to the hollow interior 3145 of the rotor shaft 314 through the gap S70 of the spline fitting portion 70. This eliminates the need to make the input shaft 31 hollow, as opposed to a conventional configuration (not shown) in which oil is supplied to the hollow interior of the rotor shaft via a hollow input shaft. In this case, the processing cost of the input shaft 31 can be reduced compared to when the input shaft 31 is realized as a hollow rotating shaft member (i.e., a rotating shaft member having a hollow interior that forms an oil passage). Furthermore, the disadvantages that can arise when the input shaft 31 is realized as a hollow rotating shaft member (issues related to the strength / rigidity of the input shaft 31) do not occur. However, even in this embodiment, the input shaft 31 can be realized as a hollow rotating shaft member for another purpose, which increases the design freedom of the input shaft 31.

[0157] In this embodiment, only one oil passage 81 is provided, but two or more oil passages may be provided. In addition, in this embodiment, the oil passage 81 is provided substantially parallel to the vertical direction, but it may be provided at an angle to the vertical direction as long as the downward gravity is applied to the oil.

[0158] Fig. 18 is a cross-sectional view showing a portion of a spline fitting portion 70B according to another modified example. In the example shown in Fig. 18, the spline fitting portion 70B between the input shaft 31 and the rotor shaft 314B has a female spline 71B with a toothless portion 712B. In this case, the toothless portion 712B can increase the gap S70B of the spline fitting portion 70B, which effectively promotes the flow of oil (see arrow R506 in Fig. 15) from the space portion 85 (see Fig. 15) through the gap S70B to the hollow interior 3145 of the rotor shaft 314B.

[0159] In this way, one or more missing teeth portions such as the missing tooth portion 712B may be formed depending on the required amount of oil to be supplied to the hollow interior 3145 of the rotor shaft 314. In the example shown in Fig. 18, the female spline 71B has the missing tooth portion 712B, but instead of or in addition to this, the male spline 72B may have a similar missing tooth portion.

[0160] The manner in which oil is supplied via the spline fitting portion 70 according to the third embodiment can also be applied to the first and second embodiments.

[0161] Next, a vehicle driving device 100C according to another embodiment will be described with reference to Fig. 19. In the following description, components that may be the same as those in the vehicle driving device 100B according to the embodiment described above will be assigned the same reference numerals, and descriptions thereof may be omitted.

[0162] Fig. 19 is a schematic cross-sectional view showing an overview of the entire rotating electric machine 1C according to another embodiment. In Fig. 19, like Fig. 14, a part of the case 2C is omitted, and the input shaft 31 and the like are also shown as components other than the rotating electric machine 1C.

[0163] A vehicle drive device 100C according to another embodiment differs from the vehicle drive device 100B according to the above-described embodiment in that the rotating electric machine 1B and case 2 are replaced with a rotating electric machine 1C and case 2C, respectively.

[0164] The rotating motor 1C of this embodiment differs from the rotating motor 1B of the above-mentioned embodiment in that it is an embedded magnet type, specifically, in that the rotor 310 is replaced with a rotor 310C and the slip ring 318 is omitted.

[0165] The rotor 310C differs from the rotor 310 of the above-described embodiment in that the rotor core 312 is replaced with a rotor core 312C, and a permanent magnet 315 is provided instead of the field winding 316.

[0166] Rotor core 312C differs from rotor core 312 of the above-described embodiment in that, instead of teeth 3122 around which field winding 316 is wound, rotor core 312C is provided with axial magnet holes 3124C into which permanent magnets 315 are inserted.

[0167] Permanent magnets 315 are inserted into magnet holes 3124C of rotor core 312C. Alternatively, permanent magnets 315 may be attached to the outer circumferential surface of rotor core 312C. The arrangement of permanent magnets (not shown) is arbitrary.

[0168] Case 2C differs from case 2 of the above-described embodiment in that second cover member 253 is eliminated, motor case 250 is replaced with motor case 250C, and first cover member 252 is replaced with first cover member 252C. Note that second cover member 253 is omitted due to the omission of slip ring 318.

[0169] The motor case 250C differs from the motor case 250 of the above-described embodiment in that the partition wall 2502 is replaced with a partition wall 2502C, and in that an axial internal case oil passage 87C is provided.

[0170] The partition wall portion 2502C differs from the partition wall portion 2502 of the above-described embodiment in that the oil passage 81 is replaced with an oil passage 81C.

[0171] The function of oil passage 81C is substantially the same as that of oil passage 81 in the above-described embodiment, but differs in that one end of the upper side is connected to in-case oil passage 87C. Accordingly, in this embodiment, oil passage pipe 82 in the above-described embodiment is omitted. However, in this embodiment, partition wall 2502C may also have a configuration similar to that of partition wall 2502 in the above-described embodiment, and in this case, oil passage pipe 82 may be provided instead of in-case oil passage 87C.

[0172] 19, the case internal oil passage 87C may be formed in a mode of extending in the axial direction in the peripheral wall portion of the motor case 250C that defines the gear accommodating chamber SP2. One end of the case internal oil passage 87C on the X2 side in the X direction is connected to the oil passage 81C, and the other end on the X1 side in the X direction is connected to the oil pump 80.

[0173] The first cover member 252C is not essentially different from the first cover member 252 of the above-described embodiment, except for a change in form due to the omission of the slip ring 318. The first cover member 252C does not need to have an oil passage structure, similar to the first cover member 252 described above.

[0174] This embodiment also provides the same effects as the above-described embodiments. That is, this embodiment also allows oil to be supplied from the X1 side of the rotor shaft 314 in the X direction to the hollow interior 3145 of the rotor shaft 314 via the space 85 and the spline fitting portion 70. This simplifies or eliminates the oil passage structure on the X2 side of the rotor shaft 314 in the X direction. As a result, compared to the conventional technology in which oil is supplied from the X2 side of the rotor shaft 314 in the X direction (the side not connected to the rotating electric machine 1B), space is saved on the X2 side of the rotor shaft 314 in the X direction, thereby enabling a reduction in the size of the rotating electric machine 1C in the X direction.

[0175] In this embodiment, the oil jetted radially from oil hole 8311B and oil hole 8312B hits coil end portions 3221 and 3222 of stator 320, thereby cooling coil end portions 3221 and 3222. In this embodiment, the oil flowing along the inner circumferential surface of hollow interior 3145 of rotor shaft 314 can also contribute to cooling permanent magnets 315.

[0176] Although each embodiment has been described in detail above, it is not limited to the specific embodiment, and various modifications and changes are possible within the scope of the claims. It is also possible to combine all or a plurality of components of the above-described embodiments.

[0177] For example, in the first embodiment described above, the oil line pipes 861 and 862 are preferably provided, but one of the oil line pipes 861 and 862 may be omitted. This also applies to the other embodiments described above. [Explanation of symbols]

[0178] 1··· Rotating electric machine, 310··· Rotor (rotor), 312··· Rotor core (core member), 314··· Rotor shaft (shaft), 3145··· Hollow interior (interior), 316··· Field winding, 3161, 3162··· Coil turn portion, 313, 313A··· End plate (end member), 3134··· Wall portion, 317, 317A··· End ring (cover member), 3170··· Peripheral wall portion, 3172··· Circumferential wall portion, 31702··· Hole portion (second hole portion), 320··· Stator (stator), 322··· Stator coil (coil), 3221, 3222··· Coil end portion (axial end portion of coil), 3210· Teeth portion, 8311, 8312, oil hole portion (first hole portion), 834, oil passage (first refrigerant passage), 8341, first passage portion, 8342, second passage portion, 8343, discharge port, 861, 861A, 862, 862A, oil passage pipe (first refrigerant pipe portion), 8610, 8610A, 8620A, 8620A, spray Outlet (first jet port), 81··· oil passage (second refrigerant pipe section), 81A··· pipe section (second refrigerant pipe section), 82··· oil pipe (second refrigerant pipe section), 87A··· pipe section (second refrigerant pipe section), 89··· oil passage (second refrigerant flow path), 890··· oil passage (fourth flow path section), 891··· oil passage (third flow path section), 80··· oil pump (pump)

Claims

1. a stator having teeth and coils wound around the teeth; a rotor having a hollow shaft and a core member around which a field winding is wound and which is fixed coaxially to the shaft, the rotor being disposed coaxially with the stator with a gap provided in the radial direction; a refrigerant flow path structure communicating with a pump that pumps the liquid refrigerant; the field winding includes a coil turn portion located at an axial end of the rotor, the refrigerant flow path structure includes a first refrigerant flow path communicating with an interior of the shaft, the first refrigerant flow path extends radially outward from the shaft, passing axially inward of the coil turn portion, and has a discharge port at a radially outer end thereof that faces the stator in the radial direction; The liquid refrigerant pumped by the pump is supplied to at least the inside of the shaft.

2. The rotating electric machine according to claim 1 , wherein the discharge port is radially opposed to an axial end of the coil of the stator.

3. the rotor further includes an end member covering an axial end surface of the core member, a part of an axially inner surface of the end member abuts against an axial end face of the core member in the axial direction, and an axially outer surface of the end member contacts the field winding; The rotating electric machine according to claim 1 , wherein the first coolant flow passage is formed between an axially inner surface of the end member and an axial end face of the core member.

4. The rotating electric machine according to claim 1 , wherein the first refrigerant flow path includes a first flow path portion extending in an annular shape and a plurality of second flow path portions extending radially outward from the first flow path portion.

5. The shaft has an outer periphery formed with one or more radial first holes, The rotating electric machine according to claim 4 , wherein one or more of the first hole portions are continuous at a radially outer side with the first flow passage portion.

6. 6. The rotating electric machine according to claim 5, wherein the circumferential position of one or more of the first hole portions coincides with the circumferential position of at least one of the plurality of second flow path portions, or is offset circumferentially with respect to the plurality of second flow path portions.

7. the refrigerant flow path structure further includes a first refrigerant pipe section having a first outlet at a position axially opposing the coil turn portion of the field winding, and a second refrigerant pipe section capable of supplying the liquid refrigerant from an axial end of the shaft to the inside of the shaft, The liquid refrigerant supplied to the first refrigerant pipe portion is ejected in the axial direction from the first ejection port of the first refrigerant pipe portion, The rotating electric machine according to claim 1 , wherein the liquid refrigerant supplied to the second refrigerant pipe section is supplied to the stator via the first refrigerant flow path.

8. the rotor further includes an end member that covers an axial end surface of the core member, and a cylindrical cover member that covers the coil turn portion and the end member from the radially outer side, The rotating electric machine according to claim 7 , wherein the first outlet of the first refrigerant pipe portion faces an axial end surface of the cover member.

9. the rotor further includes an end member that covers an axial end surface of the core member, and a cylindrical cover member that covers the coil turn portion and the end member from the radially outer side, The liquid refrigerant is ejected from the first ejection port in the axial direction onto the coil turn portion, The shaft has an outer periphery formed with one or more radial first holes, 8. The rotating electric machine according to claim 7, wherein the liquid refrigerant sprayed from the first spray port onto the coil turn portion and the liquid refrigerant sprayed from the first hole onto the coil turn portion pass through a second refrigerant flow path relating to a gap between the coil turn portion or the end member and the cover member, and is supplied to the axial end of the coil of the stator.

10. the cover member has a peripheral wall portion extending circumferentially and axially radially outside the coil turn portion, and an annular wall portion extending radially inward from an axial end of the peripheral wall portion, the annular wall portion faces the coil turn portion in the axial direction from an axially outer side, The rotating electric machine according to claim 9 , wherein the second refrigerant flow path includes a third flow path portion formed by a gap between the annular wall portion and the coil turn portion in the axial direction.

11. The rotating electric machine according to claim 10 , wherein the first outlet of the first refrigerant pipe portion is located radially inward of the annular wall portion.

12. the end member has a wall portion that stands in the axial direction in a manner that faces the coil turn portion from the radial outside, the cover member has a second radial hole portion at a position radially opposed to an axial end portion of the coil of the stator, the second refrigerant flow path includes a fourth flow path portion formed by a gap between the peripheral wall portion and the wall portion in a radial direction, The rotating electric machine according to claim 10 or 11, wherein one end of the fourth flow path portion communicates with the third flow path portion and the other end of the fourth flow path portion communicates with the second hole portion of the cover member.

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