JP5583254B2 - Lubrication cooling structure of electric motor - Google Patents

Description

  The present invention relates to a lubricating cooling structure for an electric motor that lubricates and cools each part with a liquid.

2. Description of the Related Art In a vehicle electric motor or the like, there is known one that performs cooling of a mechanical moving part such as a bearing and cooling of a heat generating part such as a rotor and a stator with a common lubricating coolant (for example, see Patent Document 1).
In the electric motor described in Patent Document 1, an annular stator is fixedly installed on a housing, a rotor disposed on an inner peripheral side of the stator via an air gap is coupled to a rotor shaft, and the shaft is coupled via a bearing. A support wall of the housing is rotatably supported. A supply passage for the lubricating coolant is provided in the rotor shaft along the axial direction, and a supply for supplying the lubricating coolant to the bearing, the rotor and the stator is provided at a position close to the bearing of the rotor shaft. Mouth is formed. The supply port of the rotor shaft is formed at a position offset to the outer side in the axial direction of the rotor with respect to the bearing. The lubricating cooling liquid is supplied to the bearing from the outer side in the axial direction, and the lubricating cooling liquid that has passed through the bearing is supplied to the rotor. It is designed to supply inside. The lubricating coolant supplied to the rotor is discharged to the outside of the housing through the rotor and the stator, and cools the rotor and the stator in the meantime.

Japanese Patent No. 3770107

  However, in this conventional lubricating cooling structure for an electric motor, it is possible to improve the lubricating performance of the bearing and the cooling performance of the rotor and stator by increasing the flow rate of the lubricating coolant discharged from the supply port. When a large amount of the supplied lubricating coolant flows along the axial end face of the rotor and flows into the air gap between the stator and the rotor, the viscosity of the lubricating coolant increases the rotational friction of the rotor.

  Accordingly, the present invention can prevent a large amount of lubricating coolant from flowing into the air gap between the stator and the rotor, thereby improving the lubrication performance and the cooling performance without increasing the rotational friction of the rotor. An object of the present invention is to provide a lubricating cooling structure for an electric motor.

  The invention according to claim 1, which solves the above problem, includes an annular stator (for example, a stator 14 in an embodiment described later) fixed to a housing (for example, a housing 11 in an embodiment described later), A rotor (for example, a rotor 15 in an embodiment described later) that is rotatably arranged on the circumferential side via an air gap, and a rotor shaft (for example, a rotor shaft 16 in an embodiment described later) that rotates integrally with the rotor. A support wall (for example, a support wall 60 and a sensor support wall 61 in an embodiment to be described later) extending to the housing at a position facing the axial end faces of the stator and the rotor, and the rotor shaft on the support wall Bearings that are rotatably supported (for example, bearings 17a and 17b in the embodiments described later), the bearings and the row In the lubricating cooling structure for an electric motor, the rotor includes a rotor base (for example, described later) that connects a rotor yoke (for example, a rotor yoke 42 in an embodiment described later) to the rotor shaft. The rotor base 40), and the rotor base extends radially outward from the inner cylinder (for example, a boss part 43 in an embodiment described later) fixed to the rotor shaft. An extending portion that protrudes, a first outer cylinder portion that is formed so as to protrude on one side in the axial direction of the extending portion, and a second portion that is formed so as to protrude on the other side in the axial direction of the extending portion. A through hole (for example, a through hole 46 in an embodiment described later) penetrating the extended portion from one side in the axial direction to the other side is formed in the extended portion. The second outer cylinder A radius of the inner circumferential surface of the first outer cylinder portion is larger than a radius of the inner circumferential surface of the first outer cylinder portion, and the oil passage has a supply port for supplying the lubricating coolant from one side in the axial direction of the extending portion. And the lubricating coolant is guided from the inner peripheral surface of the first outer cylinder portion to the inner peripheral surface of the second outer cylinder portion through the through hole.

According to a second aspect of the present invention, in the lubricating cooling structure for an electric motor according to the first aspect, the inner wall surface of the through hole is an inclined surface (for example, described later) whose diameter increases from one side in the axial direction toward the other side. It has the guide slope 46a) in the embodiment.
As a result, most of the lubricating coolant that has flowed into the rotor is discharged to the other end of the rotor along the inclined surface as the rotor rotates.

According to a third aspect of the present invention, a neutral point bus ring (for example, a neutral point bus ring 105 in an embodiment described later) is provided at a position closer to the radially inner side of the end face in the axial direction of the stator. In the lubricating cooling structure for an electric motor according to claim 2, the neutral point bus ring is disposed at an end portion on one end side in the axial direction of the rotor, which is positioned closer to a radially inner side of the inclined surface. .
On the end face in the axial direction of the stator where the neutral point bus ring is arranged, the flow of the lubricating coolant is inhibited by the neutral point bus ring and the member holding the bus ring, but the neutral point bus ring is inclined. Therefore, the positive discharge of the lubricating coolant is not hindered.

According to a fourth aspect of the present invention, in the lubricating cooling structure for an electric motor according to the second or third aspect, an outer peripheral corner on the other end side of the rotor from which the lubricating cooling liquid is discharged (for example, an outer peripheral corner in an embodiment described later) The corner 54a) has an edge shape.
As a result, the lubricating coolant is easily blown radially outward at the edge-shaped portion of the outer peripheral corner on the other end side of the rotor.

According to a fifth aspect of the present invention, in the lubricating cooling structure for an electric motor according to any one of the second to fourth aspects, the through-hole has a thickness of the rotor from one end side to the other end side in the axial direction of the rotor. And the thickness of the circumferential position corresponding to the part where the magnets are arranged on the rotor is partially thinned.
Thus, in the region on one end side in the axial direction of the rotor, the thick portion of the rotor is cooled with a low-temperature lubricating coolant before heat exchange, and in the region on the other end side of the rotor, the heat on the upstream side is cooled. The thin portion of the rotor is cooled by the lubricating coolant slightly heated by the replacement. Moreover, since the thickness of the circumferential direction position corresponding to the site | part where the magnet on a rotor is arrange | positioned is partially thin, it becomes easy to cool a magnet through the thin part.

  According to a sixth aspect of the present invention, in the lubrication and cooling structure for an electric motor according to any one of the second to fifth aspects, the stator includes a plurality of core blocks having a substantially sectoral cross section (for example, a core in an embodiment described later). Block 88), an insulating member (for example, an insulator rubber 90 in an embodiment described later) attached to each core block, and a stator coil (for example, wound around each core block via the insulating member). A plurality of core blocks around which the stator coil is wound via the insulating member, arranged in an annular shape, and attached to the core block. The inner peripheral wall (for example, the inner ring in an embodiment described later) is formed by contacting and connecting the end portions on the other end side in the axial direction of the insulating member to be adjacent to each other. Characterized in that the formation of the wall 97)

According to a seventh aspect of the present invention, in the lubricating cooling structure for an electric motor according to the sixth aspect, the plurality of core blocks are arranged in an annular shape to form a substantially cylindrical stator holder (for example, in an embodiment described later). The stator holder 93) is press-fitted into the inner periphery, the stator holder is fixed to the housing, and the axial end of the core block and the stator coil are covered on the other axial end of the stator holder. An annular end wall (for example, an annular end wall 93b in an embodiment described later) is extended, and the annular inner peripheral wall is fitted to the annular end wall so as to overlap from the radially inner side. And
Lubricating coolant flows from one end side to the other end side in the axial direction along the guide inclined surface of the rotor, and the lubricating coolant flows from the other end side of the rotor to the annular inner peripheral wall of the radially outer insulating member and the annular end of the stator holder. It may flow into the fitting part with the part wall. At this time, since the annular inner peripheral wall overlaps the annular end wall from the radially inner side, the end of the annular inner peripheral wall does not face the lubricating coolant flow direction.

  According to an eighth aspect of the present invention, there is provided a lubrication and cooling structure for an electric motor according to the sixth or seventh aspect, wherein the insulating member to be attached to each of the core blocks is divided in the axial direction (for example, an implementation described later). In the portion facing the air gap between the rotor and the stator, the axially divided piece on the one end side from the radially inner side with respect to the divided piece on the other end side is formed. It is characterized by being configured to overlap.

According to a ninth aspect of the present invention, in the lubrication and cooling structure for an electric motor according to any one of the second to eighth aspects, the housing is disposed at a position facing the other end surface in the axial direction of the stator and the rotor. A sensor support wall (for example, a sensor support wall 61 in an embodiment described later) extending radially inward from the outer peripheral wall is provided, and the bearing (for example, a bearing 17b in an embodiment described later) is provided on the sensor support wall, The bearing is attached to the sensor support wall so as to wrap in the axial direction with the inner peripheral surface of the rotor, and a rotation sensor (for example, a resolver 20 in an embodiment described later) for detecting the rotation of the rotor shaft It is attached to the axial end of the sensor support wall opposite to the bearing.
As a result, the bearing is attached to the sensor support wall so as to wrap in the axial direction with the inner peripheral surface of the rotor, and the rotation sensor is attached to the end of the sensor support wall on the opposite side of the bearing in the axial direction. Thus, the rotation sensor is not greatly separated in the axial direction.

  According to a tenth aspect of the present invention, in the lubricating cooling structure for an electric motor according to the ninth aspect, a lubricating coolant discharge port (for example, an inner discharge port 83 and an outer discharge port 84 in an embodiment described later) is provided in the sensor support wall. ).

  According to the first aspect of the present invention, a large amount of lubricating cooling liquid can be prevented from flowing into the air gap between the stator and the rotor, and the lubrication performance and the cooling performance can be improved without increasing the rotational friction of the rotor. Can be achieved.

  According to the second aspect of the present invention, the lubricating coolant flowing into the rotor from the rotor shaft can be discharged to the other end side in the axial direction of the rotor along the inclined surface by the centrifugal force accompanying the rotation of the rotor. Therefore, it is possible to more reliably prevent a large amount of lubricating coolant from flowing around the end surface on one end side of the rotor and flowing into the gap between the stator and the rotor. Therefore, it is possible to further improve the cooling performance of the rotor and reduce the friction.

  According to the third aspect of the present invention, since the neutral point bus ring is disposed at the end on the one end side in the axial direction that is located closer to the inside in the radial direction of the guide slope, positive discharge of the lubricating coolant is prevented. It is possible to prevent the neutral point bus ring and the member holding the bus ring from being obstructed, and improve the discharge performance of the lubricating coolant from the inside of the rotor.

  According to the fourth aspect of the invention, since the outer peripheral corner portion on the other end side of the rotor from which the lubricating coolant is discharged is formed in an edge shape, the lubricating coolant is cut off at the outer peripheral corner on the other end side of the rotor. Thus, the lubricating coolant can be prevented from entering the air gap between the stator and the rotor from the outer peripheral corner along the outer peripheral surface of the rotor.

  According to the fifth aspect of the present invention, since the hole is formed so that the thickness of the rotor becomes thinner from the one end side in the axial direction toward the other end side, the rotor is uniformly and efficiently cooled in the entire area in the axial direction. Moreover, since the hole is formed so that the thickness of the circumferential position corresponding to the part where the magnet is arranged on the rotor is partially thinned, the magnet part that is likely to generate heat can be efficiently cooled. Can do.

  According to the seventh aspect of the present invention, since the annular inner peripheral wall of the insulating member is fitted to the annular end wall of the stator holder so as to overlap from the radially inner side, the end of the annular inner peripheral wall is the lubricating coolant. It is possible to prevent the annular inner peripheral wall from being turned over by the flow of the lubricating coolant. Therefore, the discharge property of the lubricating coolant can be maintained satisfactorily.

  According to the eighth aspect of the invention, since the split piece on one end side in the axial direction of the insulating member overlaps the radially inner side of the split piece on the other end side, the end of the split piece on the one end side in the axial direction is lubricated. It is possible to prevent the flow of the cooling liquid from being hindered and the end portions of the divided pieces from being turned up by the flow of the lubricating cooling liquid. Therefore, in this case as well, the discharge performance of the lubricating coolant can be maintained well.

  According to the ninth aspect of the present invention, the bearing is attached to the sensor support wall so as to wrap in the axial direction with the inner peripheral surface of the rotor, and the rotation sensor is disposed at the axial end of the sensor support wall opposite to the bearing. Since the rotation sensor is disposed at a position close to the rotor in the axial direction, the axial length of the entire electric motor can be shortened.

  According to the tenth aspect of the present invention, since the lubricating coolant discharge port is formed in the sensor support wall, the discharge port can be easily formed at a desired position together with the sensor mounting hole and the like.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic configuration diagram of a vehicle drive system using an electric motor according to an embodiment of the present invention. The longitudinal cross-sectional view of the drive device with which the electric motor of the embodiment was integrated. The longitudinal cross-sectional view of the electric motor of the embodiment. The expanded sectional view of the electric motor of the embodiment. The longitudinal cross-sectional view of the electric motor of the embodiment. The longitudinal cross-sectional view of the rotor base | substrate of the embodiment. The A arrow directional view of FIG. 6 of the rotor base | substrate of the embodiment. The expanded sectional view of the edge part of the axial direction of the rotor of the embodiment. The front view which looked at the sensor support wall of the embodiment from the outer end surface. The perspective view which looked at the stator of the embodiment from the radial direction inner side. Sectional drawing corresponding to the BB cross section of FIG. 10 of the stator of the embodiment. The perspective view which looked at the insulator rubber which wound the stator coil of the embodiment from the diameter direction outside. The perspective view which looked at the insulator rubber which wound the stator coil of the embodiment from the diameter direction inner side. The side view which shows the decomposition | disassembly state of the insulator rubber of the embodiment. The top view which shows the decomposition | disassembly state of the insulator rubber of the embodiment. The front view of the insulator rubber of the embodiment. The expanded side view corresponding to the C section of Drawing 14 of the insulator rubber of the embodiment. The side view of the insulator rubber which wound the stator coil of the embodiment. Sectional drawing similar to FIG. 11 which shows other embodiment of this invention.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
The electric motor 2 according to the present invention is used, for example, in a drive device 1 for a vehicle 3 as shown in FIG.
A vehicle 3 shown in FIG. 1 is a hybrid vehicle having a drive unit 6 in which an internal combustion engine 4 and a front motor 5 are connected in series. The power of the drive unit 6 is transmitted to the front wheel Wf side via a transmission 7. On the other hand, the power of the drive device 1 provided separately from the drive unit 6 is transmitted to the rear wheel Wr side. The front motor 5 of the drive unit 6 and the motor 2 for driving the rear wheels Wr are connected to the battery 9 via a PDU 8 (power drive unit), and the power supply from the battery 9 and the motors 5 and 2 to the battery 9 are connected. Energy regeneration is performed via the PDU 8.

  FIG. 2 is a longitudinal sectional view of the entire drive device 1. In FIG. 2, 10A and 10B are left and right axles on the rear wheel side of the vehicle. The housing 11 of the drive device 1 is provided so as to cover the outer peripheral side of one axle 10B from a substantially middle position between the two axles 10A and 10B, and is supported and fixed together with the axles 10A and 10B below the rear part of the vehicle. The housing 11 is generally formed in a substantially cylindrical shape, and includes an electric motor 2 for driving an axle, a planetary gear type speed reducer 12 that decelerates the driving rotation of the electric motor 2, and the planetary gear type speed reducer. The differential device 13 that distributes the output of 12 to the left and right axles 10A and 10B is accommodated and arranged so as to be coaxial with the axles 10A and 10B.

  A substantially cylindrical stator 14 of the electric motor 2 is attached to a substantially central position in the axial direction in the housing 11, and an annular rotor 15 is rotatably disposed on the inner peripheral side of the stator 14. A rotor shaft 16 surrounding the outer periphery of the axle 10B is coupled to the inner periphery of the rotor 15, and the rotor shaft 16 can be rotated into the housing 11 via bearings 17a and 17b so as to be coaxial with the axle 10B. It is supported. A resolver 20 (rotation sensor) is provided between the outer periphery of the rotor shaft 16 and the housing 11 to feed back the rotational position information of the rotor 15 to a control controller (not shown) of the electric motor 2.

  The planetary gear type speed reducer 12 includes a sun gear 21 integrally provided on the outer periphery of one end of the rotor shaft 16, a plurality of planetary gears 22 meshed with the sun gear 21, a planetary carrier 23 that supports the planetary gears 22, And a ring gear 24 meshed with the outer peripheral side of the planetary gear 22. In the planetary gear type speed reducer 12, the driving force of the electric motor 2 is input from the sun gear 21, and the reduced driving force is output through the planetary carrier 23.

  The planetary gear 22 has a large-diameter first gear 26 that is directly meshed with the sun gear 21 and a second gear 27 that is smaller in diameter than the first gear 26. The first gear 26 and the second gear 27 are integrally formed in a state of being coaxial and offset in the axial direction. The ring gear 24 is fixedly installed at a position facing the axial direction side of the first gear 26 in the housing 11, and its inner peripheral surface is meshed with the second gear 27 having a small diameter. In the case of this embodiment, the maximum radius of the ring gear 24 is set to be smaller than the maximum distance of the first gear 26 from the center of the axle 10B.

  On the other hand, the differential 13 includes a differential case 31 in which a rotatable pinion 30 projects from the inner surface side, and a pair of side gears 32a and 32b meshed with the pinion 30 in the differential case 31. The side gears 32a and 32b are coupled to the left and right axles 10A and 10B, respectively. A planetary carrier 23 of the planetary gear reducer 12 is integrally coupled to the outer surface of the differential case 31. The differential case 31 is rotatably supported in the housing 11.

  The axle 10B includes a first shaft 34 provided with the side gear 32b of the differential device 13 at one end, a connection hub 35 coupled to the other end of the first shaft 34 so as to be integrally rotatable, and a housing 11 A differential shaft 13 and a second shaft 36 rotatably provided at the opposite axial end are provided, and the second shaft 36 is connected to a right wheel (not shown). And the connection hub 35 and the 2nd axis | shaft 36 can change now a connection state and a interruption | blocking state arbitrarily via the synchromesh mechanism 37 which is a connection / disconnection means. FIG. 2 shows a state where the connection hub 35 and the second shaft 36 are blocked in the synchromesh mechanism 37.

  The synchromesh mechanism 37 is a so-called triple cone type synchromesh mechanism, and includes three layers of friction transmission members 47 between the flange portion of the connection hub 35 and the flange portion of the second shaft 36. In the synchromesh mechanism 37, when the synchromesh 49 is operated in the direction of the connection hub 35 by the control piston 50, the three layers of friction transmission members 47 make frictional contact through the adjacent tapered surfaces. Thereby, when there is a rotational speed difference between the connection hub 35 and the second shaft 36, the rotational speed difference is gradually reduced by the frictional resistance between the tapered surfaces. When the rotational speed difference between the connection hub 35 and the second shaft 36 becomes sufficiently low and the synchro sleeve 49 is further operated in the direction of the connection hub 35, an inner spline (reference numeral) is formed on the inner peripheral surface of the synchro sleeve 49. (Not shown) meshes over the outermost spline gear (not shown) of the second shaft 36 and the outermost spline gear (not shown) of the connection hub 35. As a result, the first shaft 34, the connection hub 35, and the second shaft 36 are integrally coupled.

  On the other hand, when the synchronization sleeve 49 is operated in a direction away from the connection hub 35 by the control piston 50 from the state where the first shaft 34 and the connection hub 35 are coupled to the second shaft 36, the inside of the synchronization sleeve 49 The engagement between the spline and the spline gear of the connection hub 35 is released. Thereby, the connection between the first shaft 34 and the connection hub 35 and the second shaft 36 is cut off. The control piston 50 and the synchro sleeve 49 are moved to the connection hub 35 side by supplying high pressure oil to the connection side working chamber 57, and the second shaft 36 side is supplied by supplying high pressure oil to the release side working chamber 56. To move to.

  An oil pump 75 is fixedly installed between the electric motor 2 in the housing 11 and the synchromesh mechanism 37. The oil pump 75 is a pump that operates by receiving the driving force of the electric motor 2, and is configured by, for example, a trochoid pump. The oil pump 75 pumps lubricating coolant (hereinafter referred to as “oil”) from the bottom of the housing 11, to the working chambers 56 and 57 of the synchromesh mechanism 37, the lubricating cooling passage in the housing 11, and the tank 80. Supply to the return passage. Oil used for lubrication and cooling is collected at the bottom of the housing 11. A strainer 78 that constitutes a suction portion of the oil pump 75 is disposed at a position of the bottom portion of the housing 11 that is offset toward the vehicle front side from the rotation axis of the electric motor 2.

3 to 5 are cross-sectional views of the electric motor 2 portion of the driving device 1.
As shown in these drawings, the rotor 15 has an annular rotor yoke 42 that holds a permanent magnet 41 attached to the outer periphery of a substantially cylindrical rotor base 40 that is splined to the outer periphery of the rotor shaft 16.

FIG. 6 is a longitudinal sectional view of a single body of the rotor base 40, and FIG. 7 is a view taken in the direction of arrow A in FIG.
As shown in FIGS. 3 to 5, the rotor base 40 is provided with a boss portion 43 that is press-fitted into the rotor shaft 16 in a substantially central region in the axial direction. In addition, a small-diameter annular recess 44 and a large-diameter annular recess 45 are provided. In the outer peripheral area of the boss portion 43, a plurality of through-holes 46 having a substantially fan-shaped cross section that communicate the small-diameter annular recess 44 and the large-diameter annular recess 45 in the axial direction are provided at equal intervals in the circumferential direction. The radially outer wall of each through hole 46 is inclined so as to taper outward in the radial direction from the small-diameter annular recess 44 side toward the large-diameter annular recess 45 side, and the inclined surface has a small diameter. The guide slope 46a guides the oil flowing into the annular recess 44 to the large-diameter annular recess 45 by centrifugal force.

  Further, the through hole 46 provided in the rotor base 40 is formed corresponding to an angular region where the permanent magnet 41 on the rotor yoke 42 exists. A plurality of recesses 52 are formed in the outer peripheral surface of the small-diameter annular recess 44 in the angular region where the permanent magnet 41 on the rotor yoke 42 exists so as to continue to the through holes 46. Accordingly, the circumferential thickness of the rotor base 40 excluding the large-diameter annular recess 45 region is partially reduced corresponding to the angular region where the permanent magnet 41 exists. Further, the axial thickness of the rotor base 40 gradually decreases from the small-diameter annular recess 44 side toward the large-diameter annular recess 45 side. In this embodiment, the annular recesses 44 and 45 and the through hole 46 constitute a hole formed inside the rotor 15.

FIG. 8 is an enlarged cross-sectional view showing an axial end of the rotor 15 on the annular recess 45 side.
As shown in FIG. 3 and FIG. 3 to FIG. 5, the rotor yoke 42 is formed by stacking a plurality of annular silicon steel plates in the axial direction, and both ends of the rotor yoke 42 are prevented from being detached when fitted to the outer periphery of the rotor base 40. Has been. As shown in FIG. 8, the end of the rotor yoke 42 on the annular recess 45 side is fixed to the rotor base 40 via the end face plate 53 and the fixing ring 54, and thus the end of the fixing ring 54 to which the rotor yoke 42 is fixed. Projecting outward from the axial end of the rotor base 40. The outer peripheral corner 54a at the end of the fixing ring 54 that protrudes from the rotor base 40 has an edge shape (in this example, a right-angled edge shape). The outer peripheral corner 54a may have a more acute edge shape.

  As shown in FIGS. 2 to 5, the housing 11 has a substantially disk-like support wall 60 extending so as to partition the accommodation space of the planetary gear type reduction gear 12 and the accommodation space of the electric motor 2, A substantially disc-shaped sensor support wall 61 is attached so as to partition the accommodation space of the electric motor 2 and the accommodation space of the oil pump 75. Bearings 17a and 17b are attached to the inner peripheral surfaces of the support wall 60 and the sensor support wall 61, and the outer peripheral surface of the rotor shaft 16 is supported by the housing 11 via these bearings 17a and 17b.

  A supply passage 33 for supplying oil sent from the oil pump 75 through the inside of the axle 10 </ b> B to each part in the housing 11 is formed along the axial direction inside the rotor shaft 16. A first supply port 63 (supply port) for discharging oil from the supply passage 33 to the outside of the peripheral wall of the rotor shaft 16 adjacent to the bearings 19a and 19b on the housing space side of the electric motor 2 is provided. And a second supply port 64 (supply port) is formed. A third supply port 65 is formed at a position of the peripheral wall of the rotor shaft 16 that is offset from the first supply port 63 toward the axial center of the rotor 15.

As shown in FIGS. 3 to 5, the inner peripheral edge portion of the support wall 60 that supports one bearing 17 a is disposed so as to face the end surface in the axial direction of the rotor base 40 in the axial direction. An annular locking portion 66a that bulges toward the rotor base 40 is formed at a position opposite to. The annular locking portion 66a has an annular shape that extends from the outer side of the bearing 17a to the radially outer region of the first supply port 63 and guides the oil discharged from the first supply port 63 toward the bearing 17a. The guide member 67a is attached.
Further, the inner peripheral edge portion of the sensor support wall 61 is bent inwardly of the large-diameter annular recess 45 of the rotor base 40, and the bearing 17b is supported inside the bent portion, and an annular shape is provided at the distal end side of the bent portion. A locking portion 66b is formed. The annular locking portion 66b extends from the outer side of the bearing 17b to the radially outer region of the second projecting hole 64 and guides the oil discharged from the second supply port 64 toward the bearing 17b. A guide member 67b is attached.

Since the guide members 67a and 67b have substantially the same structure, the structure of the guide members 67a and 67b will be described below with reference to FIG. 4 showing the guide member 67a.
The guide members 67a and 67b are formed with locking portions 68 having a substantially U-shaped cross section sandwiched and fixed by the annular locking portions 66a and 66b at the outer peripheral edge, and taper out from the inner peripheral edge of the locking portion 68. The guide slope 69 is extended, and a bent end surface 70 extending radially inward is provided at the tip of the guide slope 69. An annular recess 71 that is recessed in the direction of the bearings 17a and 17b when viewed from the rotor 15 side is provided at the connecting portion between the locking portion 68 and the guide slope 69 of each guide member 67a and 67b. The annular recess 71 of the guide member 67 a on the support wall 60 side forms a labyrinth groove 72 with the end of the rotor base 40 in a state where the guide member 67 a is attached to the support wall 60.
In the case of this embodiment, the first supply port 63 and the second supply port 64 on the rotor shaft 16 are formed in an annular projection 73 portion that locks the inners of the bearings 17a and 17b, and each induction The bent end faces 70 of the members 67a and 67b extend to a position where they substantially lap in the radial direction with the end face inclined in the axial direction of the annular protrusion 73.

FIG. 9 is a front view of the sensor support wall 61 as viewed from the accommodation space side (hereinafter referred to as “outside”) of the oil pump 75.
As shown in FIG. 3, FIG. 3, and FIG. 5, a stepped surface 82 whose inner peripheral side is recessed is formed on the outer end surface of the sensor support wall 61, and the resolver 20 is attached to the stepped surface 82. . Further, the stepped surface 82 of the sensor support wall 61 is formed with arc-shaped inner discharge ports 83 (discharge ports) penetrating the sensor support wall 61 in the thickness direction. Similarly, arc-shaped outer discharge ports 84 (discharge ports) penetrating the support wall 61 in the thickness direction are formed.

  Further, an annular convex portion 85 protruding in the axial direction is provided at an intermediate position of the inner discharge port 83 and the outer discharge port 84 on the inner side surface of the sensor support wall 61, and the annular convex portion 85 is a rotor base. It arrange | positions so that the outer peripheral side of the fixing ring 54 of the edge part of 40 may be enclosed. In the sensor support wall 61, a part of the inner peripheral edge supporting the bearing 17 b enters the inside of the rotor base 40, and the inner side surface from the inner peripheral side to the outer discharge port 84 faces the end surface of the rotor 15 with a gap. . The gap between the sensor support wall 61 and the rotor 15 and the inner discharge port 83 and the outer discharge port 84 of the sensor support wall 61 have a discharge passage 86 for discharging oil from the inside of the rotor 15 to the outside of the electric motor 2. It is composed.

  In FIG. 3, main flow paths of oil discharged from the first to third discharge ports 63 to 65 of the rotor shaft 16 are indicated by arrows. Here, the main oil flow passage will be briefly described. The oil discharged from the first discharge port 63 and the second discharge port 64 is mainly guided by the guide members 67a and 67b and adjacent thereto. The remaining oil supplied to the shaft holes 17 a and 17 b and the oil discharged from the third discharge port 65 flows to the sensor support wall 61 side on the inner peripheral side of the rotor 15, and is discharged to the outside through the discharge passage 86. It has become so.

  On the other hand, as shown in FIGS. 10 and 11, the stator 14 is formed by a plurality of core blocks 88 having a substantially fan-shaped cross section butting in an annular shape, and coils on both side surfaces along the axial direction of each core block 88. A receiving slot 89 is formed. Each core block 88 is formed by laminating substantially fan-shaped silicon steel plates in the axial direction. A rectangular annular insulator rubber 90 (elastic insulating member) is attached to the core block 88 so as to surround a peripheral region passing through the coil housing slot 89, and the stator coil 91 is wound through the insulator rubber 90. ing.

  Thus, the plurality of core blocks 88 around which the stator coil 91 is wound via the insulator rubber 90 are arranged in an annular shape, and as shown in FIGS. 3 to 5, in the cylindrical peripheral wall 93 a of the stator holder 93. It is held in a press-fit state. In the stator holder 93, an annular end wall 93b that covers the axial end surfaces of the core block 88 and the stator coil 91 is extended on the bottom side of the peripheral wall 93a where the core blocks 88 are inserted. The annular end wall 93 b is abutted against the end surface of the outer peripheral edge of the sensor support wall 61 and is fastened and fixed to the sensor support wall 61 by a bolt 87. A cylindrical flange 93c that is bent in a direction facing the core block 88 is provided at the radially inner end edge of the annular end wall 93b.

FIG. 12 shows two adjacent insulator rubbers 90 around which the stator coil 91 is wound as viewed from the radially outer side, and FIG. 13 shows the same two insulator rubbers 90 as viewed from the radially inner side.
The insulator rubber 90 is configured by two divided pieces 92A and 92B divided into two in the axial direction, and a divided piece 92A arranged on the support wall 60 side and a divided piece 92B arranged on the sensor support wall 61 side. In a state of being attached to the core block 88, they are fitted to each other. 14 and 15 show a state where the divided pieces 92A and 92B of the insulator rubber 90 are divided.

The insulator rubber 90 has a flange for holding the stator coil 91 extending above and below (in the radial direction outside and inside of the stator 14) each rectangular annular side wall, and the cross section of each side wall has a channel shape. Here, the upper and lower flanges on both side walls along the axial direction of the insulator rubber 90 are referred to as an upper flange 94a and a lower flange 94b, and the upper and lower flanges on one end side (divided piece 92A side) in the axial direction are the upper end portions. When the flanges 95a and the lower end flange 95b and the upper and lower flanges on the other end side in the axial direction (divided piece 92B side) are referred to as the upper end flange 96a and the lower end flange 96b, the insulator rubber 90 adjacent in the circumferential direction The upper flanges 94a and the lower flanges 94b overlap each other. Similarly, the side edges of the upper end flange 95a on one end side in the axial direction, the side edges of the lower end flange 95b, and the axial direction The side edges of the upper end flange 96a on the other end side and the side edges of the lower end flange 96b are also overlapped. Therefore, the insulator rubber 90 has a substantially cylindrical shape in a state where all the core blocks 88 are assembled in an annular shape. The cylindrical wall formed by overlapping the lower end flanges 96b on the other end side in the axial direction of all the insulator rubbers 90 extends in the direction of the sensor support wall 61 from the vicinity of the inner peripheral end of the end face of the core block 88. An annular inner peripheral wall 97 (see FIGS. 3, 5, and 10) is formed.
In addition, as shown in FIG. 16, the uneven | corrugated | grooved part 98a, 98b with which adjacent things are engaged is formed in the side edge part of the lower end flange 96b of the other end side of an axial direction. Specifically, one lower end flange 96b to be overlaid has a concave shape on the lower surface side, and the other lower end flange 96b has a concave shape on the upper surface side. Similarly, the lower flange 94a is also provided with a concavo-convex portion that engages adjacent ones that are overlapped.

  Further, as shown in FIGS. 3 and 5, the annular inner peripheral wall 97 formed by the insulator rubber 90 is an annular end wall 93 b on the stator holder 93 side in a state where the insulator rubber 90 is assembled to the stator holder 93 together with the core block 88. The annular oil storage chamber 99 is formed so as to be overlapped with the cylindrical flange 93c from the inner side in the radial direction, thereby being surrounded by the annular end wall 93b and the annular inner peripheral wall 97. Note that an inclined surface 97a is formed in a tapered shape at the outer peripheral corner of the tip of the annular inner peripheral wall 97 (lower end flange 96b) as shown in an enlarged manner in FIG. For this reason, when the annular inner peripheral wall 97 is fitted into the cylindrical flange 93c of the annular end wall 93b, the guiding action by the inclined surface 97a can be used.

  Further, a supply hole 100 is provided at a position facing the top of the storage chamber 99 of the stator holder 93, and oil supplied from the oil pump 75 is supplied into the storage chamber 99 via the supply hole 100. ing. The oil supplied into the storage chamber 99 cools the end of the stator coil 91 facing the storage chamber 99, and a part of the oil is supplied in the axial direction of the stator 14 along the winding direction of the stator coil 91 of each core block 88. It flows out to one end side (support wall 60 side), and the others are gradually discharged to the bottom of the housing 11 through the discharge hole 101 at the lower end of the stator holder 93 as shown by the arrows in FIG.

  Further, as shown in FIGS. 12 to 14, the end portion of the insulator rubber 90 on one end side in the axial direction (the divided piece 92 </ b> A side) is branched from the lower end flange 95 b and bent downward in a substantially L shape. A bent piece 102 is extended. The bent piece 102 forms a cylindrical wall 103 (see FIGS. 3 to 5) in a state where the core block 88 is assembled in an annular shape. The cylindrical wall 103 holds the neutral point bus ring 105 that connects the neutral point of the stator coil 91 on the outer peripheral side, and the inner peripheral surface comes into close contact with the annular protrusion 104 that protrudes from the support wall 60. ing.

  Further, in a state where the stator 14 is fixed to the housing 11 (sensor support wall 61) via the stator holder 93, the stator coil 91 held by the insulator rubber 90 is exposed to one end side in the axial direction of the stator 14. However, a supply hole 106 through which oil supplied from the oil pump 75 is discharged is provided in the support wall 60 at a position opposite to the uppermost position of the exposed portion of the stator coil 91. The oil discharged from the supply hole 106 flows downward along the end of the insulator rubber 90 connected in an annular shape from the position of the uppermost stator coil 91 as shown by the arrow in FIG. The end surface of the coil 91 is cooled and discharged to the bottom of the housing 11. At this time, the oil flowing out from the storage chamber 99 on the other end side in the axial direction of the stator 14 to the one end side along the winding direction of each stator coil 91 also extends along the end portion of the insulator rubber 90 connected in an annular shape. It is discharged downward.

  In this electric motor 2, the space in the housing 11 sandwiched between the support wall 60 and the sensor support wall 61 is annularly connected, and the housing 90 accommodates the stator 14 on the outer peripheral side and the rotor 15 on the inner peripheral side. The oil for cooling the stator coil 91 separated into the space flows only in the housing space of the stator 14 on the outer peripheral side. For this reason, the oil for cooling the stator coil 91 does not flow into the air gap G between the stator 14 and the rotor 15.

  By the way, each insulator rubber 90 is constituted by the two divided pieces 92A and 92B as described above, and as shown in FIGS. 14 and 15, the concave portion 107 formed at the end of the divided piece 92A is provided at the end of the divided piece 92B. The formed convex portion 108 is fitted and connected. The split pieces 92A and 92B have an outer surface that is substantially flush with the concave portion 107 and the convex portion 108. In each insulator rubber 90, the end of the split piece 92A disposed on the support wall 60 side is disposed on the sensor support wall 61 side on the radially inner surface facing the air gap G between the stator 14 and the rotor 15. It overlaps with the edge part of the division piece 92B to be done from the inside in the radial direction.

  Further, the radially inner surface (the radially inner surface of the lower flange 84b) facing the air gap G of each insulator rubber 90 is divided into the divided piece 92B side (sensor support wall) as shown in FIGS. The end in the axial direction on the 61st side is inclined so that the end in the axial direction on the other split piece 92A side (the support wall 60 side) is more radially outward. FIG. 18 shows the insulator rubber 90 disposed at the lowermost position when attached to the housing 11 via the stator holder 93 together with the horizontal reference line R along the axial direction of the stator 14. And the insulator rubber 90 disposed in the vicinity thereof has an end in the axial direction on the side of the split piece 92B inclined more downward than an end in the axial direction on the side of the other split piece 92A. Therefore, the oil dropped on the surface facing the air gap G of the insulator rubber 90 disposed in the lowermost position and in the vicinity thereof, as indicated by the arrow in FIG. 5, is on the sensor support wall 61 side along the inclination of the surface. To be discharged.

  Here, the end portions of the split pieces 92A and 92B are fitted so that the split piece 92A side overlaps the split piece 92B from the inside in the radial direction as described above. When the oil flows from the support wall 60 side toward the sensor support wall 61 as shown by the arrow in FIG. 5, the oil flow does not turn up the joint 109 of the split pieces 92A and 92B.

  In the case of this embodiment, the surface of the insulator rubber 90 facing the air gap G is simply inclined in the axial direction. However, as in the second embodiment shown in FIG. The fluidity of the oil may be enhanced by inclining the lower flange 94b of the adjacent insulator rubber 90 radially inward.

  In the above configuration, when the oil discharged from the oil pump 75 is discharged into the electric motor 2 from the first supply port 63 and the second supply port 64 of the rotor shaft 16, the oil is discharged from both the supply ports 63 and 64. The oil thus applied hits the guide slope 69 of the annular guide members 67a and 67b and is supplied to the bearings 17a and 17b along the guide slope 69. The oil supplied to the bearings 17a and 17b passes through the inside and is discharged to the outside of the support walls 60 and 61 through the bearings 17a and 17b.

The oil discharged from the first and second supply ports 63 and 64 and overflowing from the bent end portions 70 of the guide members 67a and 67b flows out to the inner peripheral surface side of the rotor 15 (rotor yoke 42) by centrifugal force. On the other hand, the oil discharged from the third supply port 65 of the rotor shaft 16 directly flows into the inner peripheral surface of the annular recess 44 of the rotor 15.
The oil that has flowed into the inner peripheral surface of the rotor 15 through the third supply port 65 and the first and second supply ports 63 and 64 in this way is subjected to the centrifugal force associated with the rotation of the rotor 15, and most of the oil in the rotor 15. It flows in the direction of the sensor support wall 61 along the axial inclination (guide slope 46) of the inner peripheral surface, and during this time, the rotor 15 is cooled from the inner peripheral side.

  Note that some of the oil that has flowed into the inner peripheral surface of the rotor 15 may wrap around the end portion of the rotor 15 on the support wall 60 side. At this time, most of the oil is in contact with the annular recess 71 of the guide member 67a and the rotor. Captured by the labyrinth groove 72 between the 15 ends. Therefore, a large amount of oil does not flow around the end surface of the rotor 15 on the support wall 60 side and suddenly flow into the air gap G. Further, since the labyrinth groove 72 is formed in an annular shape, the oil trapped in the labyrinth groove 72 flows down vertically along the groove 72 and flows into the lower region of the air gap G. Since the radially inner surface of the insulator rubber 90 that faces the air gap G is inclined downward from the support wall 60 toward the sensor support wall 61 as described above, the oil that has flowed into the air gap G is quickly detected by the sensor support wall 61. Discharged to the side.

  The oil that has flowed out from the inner peripheral surface of the rotor 15 toward the sensor support wall 61 flows through the discharge passage 86 between the end of the rotor 15 and the sensor support wall 61, and the discharge port 83 formed in the sensor support wall 61. , 84 to the outside of the electric motor 2. During this time, the oil cools the axial end surface of the rotor 15.

  Here, between the inner discharge port 83 and the outer discharge port 84 of the sensor support wall 61, an annular convex portion 52 that protrudes toward the end surface of the rotor 15 is provided on the outer peripheral side of the fixing ring 54. Oil is discharged to the outside of the electric motor 2 through the inner discharge port 83. Further, since the outer discharge port 84 is formed at a position facing the air gap G on the outer peripheral side of the annular convex portion 85, most of the oil that flows out to the outer peripheral side of the annular convex portion 52 does not flow into the air gap G. It is discharged to the outside of the electric motor 2 through the outer discharge port 84.

  Further, since the outer peripheral side of the annular convex portion 52 is closed by the fitting portion between the annular inner peripheral wall 97 of the insulator rubber 90 and the annular end wall 93b (cylindrical flange 93c) of the stator holder 91, the outer discharge port 84 is closed. The oil flowing out flows from the annular inner peripheral wall 97 side toward the annular end wall 93b. At this time, since the annular inner peripheral wall 97 is overlapped and fitted to the annular end wall 93b from the radially inner side, the end of the annular inner peripheral wall 97 does not face the oil flow. For this reason, the end of the annular inner peripheral wall 97 is not turned up by the flow of oil.

  As described above, the electric motor 2 used in the driving device 1 has the first and second supply ports 63 and 64 formed at positions closer to the rotor 15 than the bearings 17a and 17b of the rotor shaft 16, and the bearings 17a and 17b. Since the annular guide members 67a and 67b extending from the inner peripheral edge of the support walls 60 and 61 that support the outer peripheral side region of the adjacent supply ports 63 and 64 are provided, the discharge from each of the supply ports 63 and 64 is performed. It is possible to flow most of the oil in the direction of the adjacent bearings 17a and 17b, and to suppress the amount of oil flowing in the gap direction between the rotor 15 and the support wall 60.

Further, in this electric motor 2, the guide member 67 a on one end side in the axial direction extends to a position where it wraps in the axial direction with the rotor 15, so that the oil that flies radially outward from the end of the guide member 67 a Directly flowing into the gap between the support wall 60 and the support wall 60 can be prevented.
In particular, in the case of this embodiment, the guide member 67a has a tapered tapered guide slope 69 covering the outer peripheral area of the first supply port 63, and the guide slope 69 has an annular protrusion 73 on the rotor shaft 16 side in the radial direction at the tip. Since the bent end surface 70 is extended so as to wrap, the amount of oil sneaking to the outer peripheral surface side of the guide member 67 can also be reduced.

  Further, in this embodiment, since the guide member 67 a is provided with the annular recess 71 that forms the labyrinth groove 72 with the end surface of the rotor 15, the support wall 60 and the rotor 15 are formed from the inner peripheral surface side of the rotor 15. The oil that tries to enter the gap between the two can be captured by the labyrinth groove 72 and a large amount of oil can be prevented from entering the gap suddenly.

  In the electric motor 2, a small-diameter annular recess 44 is formed at the end of the rotor 15 near the support wall 60, and a large-diameter annular recess 45 is formed at the end of the rotor 15 near the sensor support wall 61. The radially outer wall of the through-hole 46 that communicates both the annular recesses 44 and 45 is inclined so as to taper out radially outward from the small-diameter annular recess 44 side toward the large-diameter annular recess 45 side. Therefore, the oil flowing into the inner peripheral side of the rotor 15 from the first to third supply ports 63 to 65 is guided toward the sensor support wall 61 by centrifugal force, and the discharge passage on the sensor support wall 61 side. 86 can be discharged to the outside. For this reason, it is possible to positively flow the oil to the inner peripheral surface of the rotor 15 and reliably cool the rotor 15 while suppressing the oil from flowing into the gap between the rotor 15 and the support wall 60.

  In the electric motor 2, the oil discharged from the supply ports 63 to 65 is prevented from flowing in a large amount in the gap direction between the rotor 15 and the support wall 60 by the above-described devices. It is possible to prevent a large amount of oil from flowing into the air gap G between the stator 14 and the rotor 15 through the gap. Therefore, an increase in rotational friction of the rotor 15 due to a large amount of oil flowing into the air gap G can be prevented.

  Further, in the electric motor 2 of this embodiment, the neutral point bus ring 105 attached to the radially inner position of the end surface of the stator 14 is disposed at the axial end portion of the stator 14 opposite to the discharge passage 86. Therefore, the positive discharge of oil from the inside of the rotor 15 through the discharge passage 86 is not hindered by the neutral point bus ring 105, the cylindrical wall 103 of the insulator rubber 90, or the like. For this reason, the oil can be discharged from the inside of the rotor 15 through the discharge passage 86.

  Further, in the electric motor 2, the annular recess 44 is formed so that the thickness of the rotor 15 (yoke base 40) gradually decreases from the axial end on the support wall 60 side toward the end on the sensor support wall 61 side. 45 and the through hole 46 are formed, the thick portion of the rotor 15 is cooled in the vicinity of the third supply port 65 into which the low-temperature oil before heat exchange is introduced, and gradually rises by heat exchange. Since the thin portion of the rotor 15 is cooled by the heated oil, the rotor 15 can be uniformly cooled throughout the entire axial direction. Further, since the thickness of the circumferential position corresponding to the portion where the permanent magnet 41 is disposed on the rotor 15 is partially thinned, the portion of the permanent magnet 41 that easily generates heat can be efficiently cooled.

  Further, in this electric motor 2, the fixing ring 54 for fixing the rotor yoke 42 protrudes in the axial direction at the end of the yoke base 40 on the sensor support wall 61 side, and the outer peripheral corner portion of the protruding fixing ring 54 has an edge shape. Therefore, the oil that has flowed into the discharge passage can be reliably blown outward at the outer peripheral corner portion, and can be prevented from flowing into the air gap G between the stator 14 and the rotor 15 along the outer peripheral surface of the fixing ring 54.

  In the case of the electric motor 2, the annular inner peripheral wall 97 of the insulator rubber 90 is fitted to the cylindrical flange 93c of the annular end wall 93b provided in the stator holder 93 on the outer peripheral side of the discharge passage 86. Since the annular inner peripheral wall 97 on the insulator rubber 90 side is overlapped with the cylindrical flange 93c on the stator holder 93 side from the radially inner side, the annular inner peripheral wall is caused to flow into the oil flow toward the outer discharge port 84. The end faces of 97 do not face each other. Accordingly, it is possible to eliminate the problem that the oil flow is obstructed by the end portion of the annular inner peripheral wall 97 or the end portion of the annular inner peripheral wall 97 is turned up by the oil flow. Thereby, the oil dischargeability is maintained well.

  Further, in the case of the electric motor 2, the surface facing the air gap G of the insulator rubber 90 disposed in the vicinity of the lowermost end has an axial end on the sensor support wall 61 side lower than an end on the support wall 60 side. Therefore, the oil that has flowed into the air gap G flows from the support wall 60 side toward the sensor support wall 61 side, but is fitted at a portion facing the air gap G of the split pieces 92A and 92B constituting the insulator rubber 90. Since the dividing wall 92A on the support wall 60 side is overlapped with the dividing piece 92B on the sensor support wall 61 side from the inside in the radial direction, the end portion of the dividing piece 92A on the support wall 60 side is subject to oil flow. They will not face each other. Therefore, also in this part, the oil flow is not obstructed by the end portion of the divided piece 92A, and the end portion of the divided wall 92A is not turned by the oil flow. Therefore, the oil discharge performance is maintained well even at this portion.

  In the electric motor 2, a bent portion is provided at the inner peripheral edge of the sensor support wall 61 so as to enter the annular recess 45 of the rotor 15 (wrap with the rotor 15 in the axial direction). Since the bearing 17b is attached to the circumferential side, and the resolver 20 that is a rotation sensor is attached to the end of the sensor support wall 61 in the axial direction opposite to the bent portion, the resolver 20 is axially disposed with respect to the rotor 15. It is possible to reduce the axial length of the entire electric motor 2 by arranging it at a position sufficiently close to the motor.

  In the case of the electric motor 2, the discharge ports 83 and 84 for discharging the oil that has cooled the rotor 15 and the stator 14 are formed in the sensor support wall 61, which is separate from the peripheral wall of the housing 11. Can be easily formed at a desired position together with the sensor mounting hole or the like.

  In addition, this invention is not limited to said embodiment, A various design change is possible in the range which does not deviate from the summary.

2 Electric motor 11 Housing 14 Stator 15 Rotor 16 Rotor shaft 17a Bearing 17b Second bearing 20 Resolver (rotation sensor)
40 rotor base 42 rotor yoke 43 boss 44, 45 annular recess 46 through hole 46a guide slope (inclined surface)
54a Perimeter corner 60 Support wall 61 Sensor support wall (support wall)
62 supply passage 63 first supply port 64 second supply port 83 inner discharge port (discharge port)
84 Outer outlet (outlet)
86 Discharge passage 88 Core block 90 Insulator rubber (elastic insulation member)
91 Stator coil 92A, 92B Split piece 93 Stator holder 93b Annular end wall 97 Annular inner peripheral wall 105 Neutral point bus ring

Claims (10)

An annular stator fixed to the housing;
A rotor disposed rotatably on the inner peripheral side of the stator via an air gap;
A rotor shaft that rotates integrally with the rotor;
A support wall extending on the housing at a position facing the axial end faces of the stator and the rotor;
A bearing for rotatably supporting the rotor shaft on the support wall;
An oil passage for supplying a lubricating coolant to the bearing and the rotor;
In the lubricating cooling structure of the motor with
The rotor includes a rotor base that connects a rotor yoke to the rotor shaft;
The rotor base is
An inner cylinder fixed to the rotor shaft;
An extending portion extending radially outward from the inner tube portion;
A first outer cylinder portion formed so as to protrude to one side in the axial direction of the extension portion;
A second outer cylinder part formed so as to protrude to the other axial side of the extension part;
With
The extension part is formed with a through hole penetrating the extension part from one side in the axial direction to the other side,
The radius of the inner peripheral surface of the second outer cylinder part is larger than the radius of the inner peripheral surface of the first outer cylinder part,
The oil passage includes a supply port for supplying the lubricating coolant from one side in the axial direction than the extending portion,
A lubricating cooling structure for an electric motor, wherein the lubricating cooling liquid is guided from an inner peripheral surface of the first outer cylinder portion to an inner peripheral surface of the second outer cylinder portion through the through hole.   The lubricating cooling structure for an electric motor according to claim 1, wherein an inner wall surface of the through hole has an inclined surface that increases in diameter from one side in the axial direction toward the other side. The lubricating cooling structure for an electric motor according to claim 2, wherein a neutral point bus ring is provided at a position radially inward of the axial end face of the stator.
A lubricating cooling structure for an electric motor, wherein the neutral point bus ring is disposed at an end portion on one end side in the axial direction of the rotor, which is positioned closer to a radially inner side of the inclined surface.   4. The lubricating cooling structure for an electric motor according to claim 2, wherein an outer peripheral corner portion on the other end side of the rotor from which the lubricating cooling liquid is discharged has an edge shape.   The through hole is formed so that the thickness of the rotor becomes thinner from one end side to the other end side in the axial direction of the rotor, and the thickness of the circumferential position corresponding to the portion where the magnet on the rotor is disposed. The lubricating cooling structure for an electric motor according to any one of claims 2 to 4, wherein the lubricating cooling structure is formed so that the thickness is partially reduced. The stator,
A plurality of core blocks having a substantially sectoral cross section;
An insulating member attached to each core block;
A stator coil wound around each of the core blocks via the insulating member;
And a structure with
The plurality of core blocks around which the stator coil is wound via the insulating member are arranged in an annular shape,
6. An annular inner peripheral wall is formed by contacting and connecting the end portions on the other end side in the axial direction of the insulating member attached to the core block with adjacent ones. 2. A lubricating cooling structure for an electric motor according to claim 1. A plurality of the core blocks are arranged in an annular shape and press-fitted into the inner periphery of a substantially cylindrical stator holder, and the stator holder is fixed to the housing,
An annular end wall covering the axial end of the core block and the stator coil is extended to the other end side of the axial direction of the stator holder,
The lubricating cooling structure for an electric motor according to claim 6, wherein the annular inner peripheral wall is fitted to the annular end wall so as to overlap from the radially inner side. The insulating member attached to each of the core blocks is constituted by divided pieces divided in the axial direction,
The part facing the air gap between the rotor and the stator is configured such that the split piece on one end side in the axial direction overlaps the split piece on the other end side from the inside in the radial direction. The lubricating cooling structure for an electric motor according to 6 or 7. A sensor support wall extending radially inward from the outer peripheral wall of the housing is provided at a position facing the other end surface in the axial direction of the stator and the rotor,
The bearing is provided on the sensor support wall,
The bearing is attached to the sensor support wall so as to wrap in the axial direction with the inner peripheral surface of the rotor, and a rotation sensor that detects the rotation of the rotor shaft is disposed on the opposite side of the bearing on the sensor support wall. The lubricating cooling structure for an electric motor according to any one of claims 2 to 8, wherein the lubricating cooling structure is attached to an end portion in an axial direction.   10. The lubricating cooling structure for an electric motor according to claim 9, wherein a discharge port for lubricating coolant is formed in the sensor support wall.

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