JP2020018112A - Stator cooling device and cooling control arrangement - Google Patents

Abstract

To improve efficiency in a cooling system realizing cooling of a coil by oil, and cooling of a stator core by cooling water.SOLUTION: A stator cooling device comprises an oil circulation part including a motor-driven oil pump, and circulating oil capable of cooling the coil of a dynamo-electric machine, a cooling water circulation part including a water pump, and circulating the cooling water in such a manner as to pass through a cooling channel formed by a wall surface part including a first wall surface part in contact with the stator core of the dynamo-electric machine, and a pump controller for bringing the motor-driven oil pump into operation state in at least a part of fist active region where the torque of the dynamo-electric machine goes above a predetermined first threshold level thereof in the operation state, and making the discharge quantity of the motor-driven oil pump into smaller than that in the operation state, in at least a part of second active region where the torque of the dynamo-electric machine goes below the first threshold level and the number of revolution of the dynamo-electric machine is larger than a predetermined second threshold level.SELECTED DRAWING: Figure 21

Description

  The present disclosure relates to a stator cooling device and a cooling control device.

  When the number of rotations of the motor is less than the threshold value, oil flows only to the coil cooling pipe for cooling the coil, and when the number of rotations is equal to or more than the threshold value, oil flows to both the coil cooling pipe and the stator cooling pipe for cooling the stator. Is known (for example, see Patent Document 1).

  Further, there is known a technique in which only a stator coil is directly cooled in an operation region where copper loss is dominant, and only a stator core is directly cooled in an operation region where iron loss is dominant (for example, see Patent Document 2).

JP 2006-353051 A JP 2005-229671 A

  However, with the above-described conventional techniques, it is difficult to improve the efficiency of a cooling system that realizes cooling of a coil by oil and cooling of a stator core by cooling water. For example, in such a cooling system, when the oil is cooled by the cooling water while circulating the oil, the cooling capacity of the stator core by the cooling water is reduced, and the stator core may not be efficiently cooled.

  Therefore, in one aspect, an object of the present invention is to improve the efficiency of a cooling system that realizes cooling of a coil by oil and cooling of a stator core by cooling water.

In one aspect, an oil circulation unit that includes an electric oil pump and circulates oil that can cool a coil of the rotating electric machine,
The cooling water is circulated in a mode including a water pump and passing through a cooling water passage formed by a wall surface portion including a first wall surface portion in contact with a stator core of the rotating electric machine and a second wall surface portion in contact with an oil passage through which the oil passes. Cooling water circulation section,
In the operating state of the water pump, in at least a part of the first operation region in which the torque of the rotating electric machine is equal to or more than a predetermined first threshold, the electric oil pump is operated, and the torque of the rotating electric machine is reduced. In at least a part of the second operation region where the rotation speed of the rotating electric machine is smaller than the first threshold value and larger than a predetermined second threshold value, the discharge amount of the electric oil pump is set to be smaller than in the operation state. A stator cooling device is provided that includes a pump control device.

  In one aspect, according to the present invention, it is possible to improve the efficiency of a cooling system that realizes cooling of a coil by oil and cooling of a stator core by cooling water.

It is a figure which shows an example of a vehicle drive device schematically. It is a figure showing roughly an example of composition of a lubrication / cooling system of a vehicle drive device. FIG. 2 is a perspective view showing an external appearance of a part of the motor. FIG. 4 is a perspective view of the holding ring viewed in the same direction as FIG. 3. FIG. 5 is a perspective view of the holding ring as viewed from an X2 side (see FIG. 4). FIG. 5 is a perspective view of the holding ring viewed from the X1 side in the X direction (see FIG. 4). FIG. 4 is a sectional view of a part of the motor shown in FIG. 3. It is an enlarged view of the P1 part of FIG. It is explanatory drawing of a case waterway. It is explanatory drawing of an inlet channel and an outlet channel. It is explanatory drawing of a meandering waterway. It is a figure showing typically the deployment state of the meandering waterway. It is sectional drawing which shows the relationship between a cooling water inlet part and an inlet waterway. FIG. 11 is a cross-sectional view of a part of the motor viewed in a direction indicated by an arrow M2 in FIG. 10. It is a perspective view which shows the upper side of a holding ring. It is sectional drawing which passes through the oil drop hole of an oil drop part. It is sectional drawing which passes through the oil drop hole of an oil drop part. It is sectional drawing which passes through the oil drop hole of an oil drop part. It is explanatory drawing of a modification. FIG. 3 is a diagram illustrating an example of a hardware configuration of a control device. It is a block diagram showing an example of a function concerning control of a stator cooling structure in a control device. FIG. 3 is an explanatory diagram of an operation area of a motor. 5 is a flowchart illustrating an example of a process executed by the control device. FIG. 11 is a block diagram illustrating another example of a function related to control of the stator cooling structure in the control device. FIG. 4 is an explanatory diagram of an operation line (contour lines related to an energizing current). 5 is a flowchart illustrating an example of a process executed by the control device.

  Hereinafter, each embodiment will be described in detail with reference to the accompanying drawings. Here, first, a vehicle drive device and a lubrication / cooling system (a lubrication / cooling system including a stator cooling structure) to which the stator cooling device can be applied will be described, and then a heat exchange and water cooling unit of the lubrication / cooling system will be described. Next, the stator cooling device will be described.

<Vehicle drive device>
FIG. 1 is a diagram schematically showing an example of a vehicle drive device 1 to which a stator cooling structure can be applied. FIG. 1 also shows the drive wheels WL and WR.

  The vehicle drive device 1 is mounted on a vehicle. The vehicle drive device 1 includes a motor 10 (an example of a rotating electric machine), a speed reduction mechanism 12, and a differential device 14 connected to the output shaft 116 of the motor 10 via the speed reduction mechanism 12. The motor 10 generates a driving force for the vehicle. The motor 10 includes a rotor 10a and a stator 10b. The stator 10b includes a stator core 112 and a coil end 110 formed by a coil (not shown) mounted on the stator 10b. In addition, the stator core 112 may be formed of, for example, a laminated steel plate. The left and right driving wheels WL and WR are connected to the differential device 14. The differential device 14 includes a ring gear 140, a pinion gear 141, and a side gear 142. Further, the differential device 14 includes a differential case (not shown) that houses gears (the pinion gear 141, the side gear 142, and the like) inside. The configuration of the reduction mechanism 12 is not limited to the illustrated simple configuration, and may include a planetary gear mechanism. Each component (the motor 10, the speed reduction mechanism 12, the differential device 14, etc.) of the vehicle driving device 1 may be incorporated in a housing (not shown) as a single vehicle driving device unit, for example, or may be a plurality of components. It may be incorporated in another housing (not shown).

  The vehicle driving device 1 includes a lubrication / cooling system 3 for lubricating and / or cooling the motor 10, the speed reduction mechanism 12, and the differential device 14 using oil. Hereinafter, “lubrication / cooling” means at least one of lubrication and cooling.

  Note that a stator cooling structure 402 (see FIG. 2) according to an embodiment described later is applied to the motor 10 of the vehicle drive device 1 shown in FIG. 1 as an example. The present invention is also applicable to a motor included in a vehicle drive device having a configuration other than the device 1. That is, a stator cooling structure 402 described later can be applied to a vehicle drive device having an arbitrary configuration including a motor such as the motor 10. Further, the present invention is also applicable to a configuration including a generator (another example of a rotating electric machine) instead of the motor.

<Lubrication and cooling system>
FIG. 2 is a diagram schematically illustrating an example of a configuration of the lubrication / cooling system 3 of the vehicle drive device 1.

  The lubrication / cooling system 3 includes a tank 30, oil passages 31 to 36, an electric oil pump 40, a mechanical oil pump 42, a heat exchange and water cooling unit 50, a water pump 90, a radiator 92, And cooling water passages 94 and 95.

  The tank 30 is formed by a lowermost portion (a lowermost space in the vertical direction) in the housing of the vehicle drive device 1. The tank 30 is formed by, for example, an oil pan. The differential device 14 is disposed in the tank 30, and the differential device 14 is immersed in the oil in the tank 30. The differential device 14 is provided at a predetermined height predetermined with respect to the lower surface of the tank 30. The predetermined height is such that when the oil level of the tank 30 is equal to or higher than a predetermined height, the oil in the tank 30 enters the differential case with the rotation of the differential device 14 (the rotation of the differential case). It is determined that lubrication and cooling of the differential device 14 in a desired manner are realized. On the lower surface of the tank 30, a strainer 30a is provided.

  The oil passage 31 is provided between the tank 30 and the suction side of the electric oil pump 40. When the electric oil pump 40 operates, the oil in the tank 30 is sucked into the suction port of the electric oil pump 40 via the strainer 30a and the oil passage 31.

  The oil passage 32 is provided between the tank 30 and the suction side of the mechanical oil pump 42. When the mechanical oil pump 42 operates, the oil in the tank 30 is sucked into the suction port of the mechanical oil pump 42 via the strainer 30a and the oil passage 32. In addition, in the example shown in FIG. 2, the oil passage 32 has a common portion with the oil passage 31, but there is no such common portion, and the oil passage 32 may be formed independently of the oil passage 31.

  The oil passage 33 is provided between the discharge side of the electric oil pump 40 and the inlet side of the heat exchange and water cooling unit 50. The oil passage 33 guides oil discharged from the electric oil pump 40 to the heat exchange and water cooling unit 50. Therefore, the oil discharged from the electric oil pump 40 is supplied to the oil passage 36 after being cooled by the heat exchange and water cooling unit 50.

  The oil passage 34 is provided between the discharge side of the mechanical oil pump 42 and the tank 30. The oil passage 34 guides oil discharged from the mechanical oil pump 42 to the tank 30. The oil passage 34 may include an oil passage formed in a member such as a shaft of a speed reduction mechanism, or a simple space. The mere space is a space in the housing of the vehicle drive device 1. The oil from the oil passage 34 is used for lubrication in a member to be lubricated (the lubricating portion 22). The lubrication portion 22 is, for example, a bearing of the motor 10 or the like.

  The oil passage 35 is connected between the oil passage 33 and the oil passage 36 so as to pass through the heat exchange and water cooling unit 50. As will be described later, the oil in the oil passage 35 is cooled by a liquid refrigerant (cooling water) passing through the cooling water passage 95. The details of the oil passage 35 will be described later.

  The oil passage 36 is provided between the outlet side of the heat exchange and water cooling unit 50 and the tank 30. The oil passage 36 guides oil from the heat exchange and water cooling unit 50 to the tank 30. The oil passage 36 may be an oil passage formed in a member, such as an oil passage formed in a shaft of a speed reduction mechanism, an oil passage formed by a pipe, or the like. 10 includes a space within the housing (eg, case 70 of FIG. 3). In this case, the oil from the heat exchange and water cooling unit 50 is dropped by gravity, supplied to a member to be cooled (the cooling part 23), and then guided to the tank 30 by gravity. The cooling part 23 includes, for example, a coil end 110 (see FIG. 1) of the stator 10b of the motor 10.

  The electric oil pump 40 is driven by a dedicated drive source (not shown) such as a motor. The electric oil pump 40 discharges oil in the tank 30 to the oil passage 33 at the time of operation. That is, the electric oil pump 40 sucks the oil in the tank 30 through the oil passage 31 and discharges the oil to the oil passage 33 during operation. The oil discharged to the oil passage 33 is guided to the oil passage 36 via the heat exchange and water cooling unit 50. The electric oil pump 40 operates independently of the rotation of the wheels, and is an electrically operated oil pump. In addition, the electric oil pump 40 forms an oil circulation unit 400 that circulates oil through the oil passage 35 together with the tank 30, the oil passage 31, the oil passage 33, and the oil passage 36. Circulation section 400 may include other elements.

  When operated, the mechanical oil pump 42 sucks oil in the tank 30 through the oil passage 32 and discharges the oil to the oil passage 34. The mechanical oil pump 42 operates in accordance with the forward rotation of the wheels (forward rotation). The mechanical oil pump 42 may be provided for an arbitrary rotating member that rotates with the forward rotation of the wheel. For example, the mechanical oil pump 42 is provided on a counter shaft of the reduction mechanism 12 (see FIG. 1), and operates by forward rotation of the counter shaft of the reduction mechanism 12.

  The heat exchange and water cooling unit 50 has both a heat exchange function and a stator core water cooling function. Specifically, the heat exchange and water cooling unit 50 has a heat exchange function of realizing heat exchange between oil in the oil passage 35 and cooling water in the cooling water passage 95, and a stator core of the stator 10 b of the motor 10. It has a function of directly cooling 112 with cooling water (stator core water cooling function). The cooling water is, for example, water containing antifreeze or LLC (Long Life Coolant).

  The heat exchange and water cooling unit 50 also functions as an oil cooler, but is not the same as an oil cooler in that it has a function of cooling the stator core 112 of the motor 10 as a function other than the function of the oil cooler. Since the lubrication / cooling system 3 includes the heat exchange / water cooling unit 50, an oil cooler separate from the heat exchange / water cooling unit 50 can be eliminated. In this embodiment, the heat exchange and water cooling unit 50 is applied to the motor 10. The details of the heat exchange and water cooling unit 50 will be described later.

  The water pump 90 is a pump that circulates cooling water through the cooling water passages 94 and 95. In addition, the water pump 90 forms a cooling water circulation unit 401 that circulates cooling water through the cooling water passage 95 together with the radiator 92 and the cooling water passage 94. However, in a modified example, the cooling water circulation unit 401 includes other elements. May be. Further, the cooling water circulation unit 401 forms the stator cooling structure 402 together with the oil circulation unit 400 and the heat exchange and water cooling unit 50 described above. However, in a modified example, the stator cooling structure 402 may include other elements.

  The radiator 92 takes heat from the cooling water passing through the cooling water passages 94 and 95 to cool the cooling water. The radiator 92 may realize heat exchange between air (for example, air passing when the vehicle travels) and cooling water.

  The cooling water passage 94 guides the cooling water discharged from the water pump 90 to the cooling water passage 95 of the heat exchange and water cooling unit 50, and transfers the cooling water from the cooling water passage 95 of the heat exchange and water cooling unit 50 via the radiator 92 to a water pump. Return to 90. The radiator 92 may be provided between the water pump 90 and the heat exchange and water cooling unit 50.

  The cooling water passage 95 is formed in the heat exchange / water cooling unit 50. When the cooling water passes through the cooling water passage 95, the heat exchange function of the heat exchange and water cooling unit 50 and the stator core water cooling function described above can be realized. The details of the cooling water channel 95 will be described later.

  In the example shown in FIG. 2, the electric oil pump 40 and the mechanical oil pump 42 are provided, but one of the electric oil pump 40 and the mechanical oil pump 42 may be omitted. In this case, the lubrication part 22 and the cooling part 23 may be lubricated and cooled by oil from the other one (not omitted) of the electric oil pump 40 and the mechanical oil pump 42 without distinction.

  In the example shown in FIG. 2, the oil passage 33 may be branched and connected to the oil passage 34. In this case, the oil from the electric oil pump 40 is also supplied to the lubrication part 22. Alternatively, the oil passage 36 may be branched and connected to the oil passage 34. In this case, the oil from the heat exchange and water cooling section 50 is also supplied to the lubrication section 22. Alternatively, the oil passage 34 may be branched and connected to the oil passage 33. Further, the oil passage 34 may be connected to and integrated with the oil passage 36 on the downstream side of the lubrication section 22 and on the downstream side of the cooling section 23.

  In the example shown in FIG. 2, the cooling water passage 94 is connected only to the heat exchange and water cooling unit 50, but a member to be cooled, for example, an inverter (not shown) for driving the motor 10, It may be formed so as to pass through a high-voltage battery (not shown) or the like that drives the motor 10.

<Heat exchange and water cooling unit>
Next, a heat exchange and water cooling unit 50 according to an embodiment applied to the motor 10 will be described with reference to FIG. In addition, in FIG. 3 and subsequent figures, from the viewpoint of maintaining the clarity of the drawing, a plurality of elements may be denoted by reference numerals only for some of the elements.

  FIG. 3 is a perspective view showing an appearance of a part of the motor 10, and FIG. 4 is a perspective view of a holding ring 60 (an example of a cooling water channel forming member) viewed in the same direction as FIG. FIG. 5 is a perspective view of the holding ring 60 viewed from the X direction X2 side (see FIG. 4), and FIG. 6 is an explanatory diagram of the inside of the holding ring 60, viewed from the X direction X1 side (see FIG. 4). It is the perspective view of the holding ring 60 seen from. FIG. 7 is a sectional view of a part of the motor 10 shown in FIG. FIG. 8 is an enlarged view of a portion P1 in FIG. FIG. 3 does not show the rotor and the like of the motor 10.

  Hereinafter, the radial direction is based on the central axis I of the motor 10 (= the central axis of the stator core 112) unless otherwise specified. Note that the axial direction of the motor 10 corresponds to the X direction. In the following description, the up-down direction indicates the up-down direction when the motor 10 is mounted so that the center axis I is substantially parallel to the horizontal direction. The cross section in FIG. 7 is a cross section taken along a plane passing through the central axis I.

  The heat exchange and water cooling section 50 includes a holding ring 60 and a case 70. The heat exchange and water cooling section 50 forms an oil passage 35 (see FIG. 2) between the holding ring 60 and the case 70 in the radial direction. Hereinafter, the “oil passage 35” is referred to as “case oil passage 35”, and the structure of the case oil passage 35 will be described later. Further, the heat exchange and water cooling unit 50 includes a cooling water passage 95 (see FIG. 2) inside the holding ring 60. The structure of the cooling water passage 95 will be described later.

  The retaining ring 60 has a cylindrical shape as shown in FIGS. The retaining ring 60 is formed of a material having good thermal conductivity such as a metal. The holding ring 60 has a structure having a hollow portion (cavity) forming a cooling water passage 95 (see FIG. 2) as described later. The holding ring 60 having such a hollow portion may be manufactured by combining a plurality of parts, or may be formed by casting.

  As shown in FIGS. 4 to 6, the retaining ring 60 includes an annular bottom portion 62 and a cylindrical portion 64 extending from the outer peripheral edge of the bottom portion 62 in the X direction. The bottom part 62 and the cylindrical part 64 may form an integral continuous part.

  The holding ring 60 has a hole 62a in the bottom surface portion 62 through which a rotor (not shown) passes. The hole 62a is formed, for example, in a circular shape around the center of the bottom portion 62 (the center through which the central axis I passes).

  As shown in FIGS. 5 and 7, the holding ring 60 further has a through hole 62b in the bottom surface portion 62. The through hole 62b is used for fixing the holding ring 60 to the case 70 by bolts. The through hole 62b is formed with a diameter through which the shaft of the bolt BT (see FIG. 7) passes. A plurality of through holes 62b are provided along the circumferential direction. At this time, the through holes 62b are formed at equal intervals along the circumferential direction. The through-hole 62b is preferably located within a radial range that does not overlap the stator core 112 when viewed in the X direction, as shown in FIG. Thereby, workability when assembling the holding ring 60 to the case 70 with the stator core 112 attached to the holding ring 60 is improved. That is, a work space for fastening the bolt BT is formed on the outer peripheral side of the stator core 112, so that workability is improved.

  As shown in FIG. 5, the retaining ring 60 further has an oil outlet hole 62c in the form of a through hole in the bottom surface portion 62. The oil outlet hole 62c is an outlet hole for oil stored in a lower portion (oil storage space) of the motor 10, and is connected to the tank 30 (see FIG. 2). The oil outlet hole 62c is preferably located below the central axis I and within a radial range that overlaps the stator core 112 when viewed in the X direction, as shown in FIG. In this case, the oil outlet hole 62c can be arranged at a position that does not restrict the formation of the through hole 62b. The oil outlet hole 62c determines the highest position of the oil stored in the oil storage space, and is set such that the highest position of the oil is lower than the lowest position of the rotor 10a. That is, the oil outlet hole 62c may be formed such that the lower end is located at a height of about the difference between the inner and outer diameters of the stator core 112.

  As shown in FIG. 5, the holding ring 60 further includes a cooling water inlet 62d and a cooling water outlet 62e on the X2 side of the bottom surface 62 in the X direction. The cooling water inlet 62d and the cooling water outlet 62e communicate with an inlet water passage 951 and an outlet water passage 952 (both described below) formed in the bottom surface 62 from the X direction X2 side of the bottom surface 62.

  The cooling water inlet 62d and the cooling water outlet 62e are provided at substantially the same radial position and adjacent in the circumferential direction, as shown in FIG. 5, for example. In the present embodiment, as an example, the cooling water inlet 62d and the cooling water outlet 62e are provided so as to be located on both sides in the circumferential direction with respect to a concave groove 641 described later. In this case, since the groove 641 is close to the cooling water inlet 62d, oil (described later) introduced into the groove 641 in the X direction can be efficiently cooled by the cooling water introduced into the cooling water inlet 62d. .

  As shown in FIG. 6, the holding ring 60 has bulging portions 62 f and 62 g which form an inlet water passage 951 and an outlet water passage 952 (both will be described later) on the X direction X1 side of the bottom surface portion 62. The bulging portions 62f and 62g are provided on the opposite sides of the cooling water inlet 62d and the cooling water outlet 62e in the X direction.

  Except for the end portion 640 of the cylindrical portion 64 on the X1 side in the X direction, the retaining ring 60 has the entire radially outer surface (outer peripheral surface) of the cylindrical portion 64 in the radial direction of the case oil passage 35 (see FIG. 2). An inner boundary surface 35b is formed. As shown in FIG. 8, the end 640 of the cylindrical portion 64 has a radially inner boundary of the case oil passage 35 (see FIG. 2) in order to secure necessary dimensions in the radial direction of the case oil passage 35. The outer diameter is larger than the surface 35b.

  As shown in FIGS. 5 and 8, the retaining ring 60 has a seal groove 640 a that is recessed radially inward on the outer peripheral surface of the end 640 of the cylindrical portion 64. The seal groove 640a extends over the entire circumference in the circumferential direction. The outer peripheral surface of the end portion 640 of the cylindrical portion 64 is in radial contact with the inner peripheral surface of the case 70 over the entire circumference in the circumferential direction. A seal material (not shown) such as an O-ring is mounted in the seal groove 640a. Thereby, between the case 70 and the holding ring 60 (the case oil passage 35) on the X direction X1 side of the cylindrical portion 64 is kept oil-tight.

  The holding ring 60 holds the stator core 112 radially inward in such a manner that the cylindrical portion 64 contacts the stator core 112 in the radial direction. That is, the retaining ring 60 retains the stator core 112 such that the inner peripheral surface of the cylindrical portion 64 contacts the outer peripheral surface of the stator core 112. For example, the retaining ring 60 is integrated with the stator core 112 by shrink fitting or the like. The retaining ring 60 is fixed to the case 70 by bolts while being integrated with the stator core 112. In this manner, the retaining ring 60 supports the stator 10b including the stator core 112 with respect to the case 70.

  The retaining ring 60 preferably retains the stator core 112 in such a manner that the inner peripheral surface of the cylindrical portion 64 contacts substantially the entire outer peripheral surface of the stator core 112. In this case, the entire stator core 112 can be efficiently cooled by the cooling water passing through the cooling water passage 95 in the retaining ring 60. In the present embodiment, as an example, as shown in FIG. 7, the holding ring 60 extends over the entire length of the stator core 112 in the X direction, and the inner peripheral surface of the cylindrical portion 64 contacts almost the entire outer peripheral surface of the stator core 112. . The “substantially the entirety” of the outer peripheral surface of the stator core 112 refers to a location such as a welding groove (not shown) of the stator core 112 (the outer peripheral surface of the stator core 112 and the inner peripheral surface of the cylindrical portion 64 are radially separated from each other. This is a concept that allows for

  As shown in FIG. 7, in the holding ring 60, the cylindrical portion 64 extends beyond the coil end 110 in the X direction on the X2 side in the X direction. On the other hand, in the present embodiment, as an example, as shown in FIG. 7, the holding ring 60 is configured such that the cylindrical portion 64 is located in the X direction on the X1 side in front of the end of the coil end 110 (the end on the X1 side). Extend to. However, in the modified example, the holding ring 60 also has the cylindrical portion 64 extending to the end of the coil end 110 (the end on the X1 side) or beyond the end in the X direction on the X1 side. Is also good.

  7, on the X2 side, the bottom surface portion 62 of the holding ring 60 faces the end surface of the stator core 112 on the X2 side in the X direction. At this time, in the present embodiment, as an example, the holding ring 60 has the bottom surface portion 62 separated in the X direction from the end of the stator 10b on the X direction X2 side (the end surface of the coil end 110 on the X direction X2 side). While facing each other. At this time, the separation distance may correspond to a required insulation distance between the coil end 110 and the holding ring 60.

  As shown in FIG. 4, the retaining ring 60 has concave grooves 641, 642, 643 recessed radially inward on the outer peripheral surface of the cylindrical portion 64. The concave grooves 641, 642, and 643 function as concave oil passages 351, 352, and 353 (described later) that form a part of the case oil passage 35 (see FIG. 2), and meandering water passages 950 (see FIG. 11) described later. Function as a circumferential partition wall (side wall).

  The concave groove 641 extends linearly in the X direction so that the X direction X2 side is open in the X direction and the X direction X1 side is closed in the X direction. The concave groove 641 extends to the end 640 of the cylindrical portion 64 on the X1 direction X1 side. The groove 641 is formed so as to be located below the grooves 642 and 643 (see also FIG. 11 described later). That is, when the motor 10 is mounted, the concave groove 641 is located in the lowermost region of the holding ring 60. The lowermost region of the retaining ring 60 represents the lowest position of the retaining ring 60 and a region in the vicinity thereof. The lowermost region may be, for example, a range of about 60 degrees in the circumferential direction around the circumferential position corresponding to the lowest position. As will be described later, the concave groove 641 forms an oil inlet 35a (an oil inlet to the case oil passage 35) of the case oil passage 35 on the X2 side in the X direction. The concave groove 641 extends in the X direction, for example, with a substantially equal cross section. The cross-sectional shape of the concave groove 641 may be slightly increased from a predetermined position in the X direction toward the X2 side in order to secure a cross-sectional area as the oil inlet portion 35a.

  The concave groove 642 extends linearly in the X direction, with the X direction X2 side opening in the X direction and the X direction X1 side closing in the X direction. The concave groove 642 extends in the X direction X1 side by a predetermined distance L1 (see FIG. 4) before the end 640 of the cylindrical portion 64. The concave groove 642 extends in the X direction, for example, with a substantially equal cross section. The predetermined distance L1 is a value that determines the width of a flow path of a meandering water channel 950 (see FIG. 11) described later, and depends on the flow of cooling water (see arrows R2 and R3 in FIG. 5) in the meandering water channel 950 (see FIG. 11). It may be determined from the viewpoint of increasing the heat exchange capacity.

  The concave groove 643 extends linearly in the X direction so that the X1 side and the X2 side in the X direction are closed in the X direction. The concave groove 643 extends to the end 640 of the cylindrical portion 64 on the X1 direction X1 side. The concave groove 643 extends a predetermined distance L2 (see FIG. 4) closer to the X2 side than the end of the cylindrical portion 64 (the end on the X2 side). The concave groove 643 extends in the X direction, for example, with a substantially equal cross section. The predetermined distance L2 may be the same as the predetermined distance L1.

  The grooves 642 and the grooves 643 are formed alternately in the circumferential direction, as shown in FIG. That is, the concave groove 642 and the concave groove 643 are formed with the concave groove 642 around the concave groove 641 in the lowermost region and in the outer circumferential direction of the concave groove 641, and each of the concave grooves 642 in the circumferential direction is formed. A groove 643 is formed on the outside, and a groove 642 is formed on the outside of each of the grooves 643 in the circumferential direction, and so on. However, as described later, the grooves 642 and 643 formed in the zenith region are integrated with oil dropping portions 356 and 358 for dropping oil to the coil end 110.

  The concave grooves 641, 642, and 643 are formed at predetermined angular intervals (30-degree intervals in this example) along the circumferential direction of the cylindrical portion 64. In the present embodiment, as an example, the concave groove 642 is formed at an interval of 60 degrees shifted from the concave groove 641 in the lowermost region by 30 degrees, and the concave groove 643 is formed with respect to the concave groove 641 in the lowermost region. It is formed at intervals of 60 degrees, shifted by 60 degrees.

  The case 70 is formed of, for example, a metal such as aluminum. The case 70 may be formed by combining two or more parts. The case 70 supports the holding ring 60 radially inward. That is, the case 70 is provided so as to cover the outside of the cylindrical portion 64 of the holding ring 60 in the radial direction, and supports the holding ring 60. The holding ring 60 may be supported in any manner, but preferably, the case 70 is held by a bolt BT (an example of a fixing member) passing through a through hole 62b of the bottom surface 62 of the holding ring 60, as shown in FIG. The ring 60 is supported. That is, the retaining ring 60 is fixed to the case 70 by the bolt BT. Thereby, for example, the diameter of the motor 10 can be easily reduced as compared with the case where the holding ring 60 includes a mounting portion (a portion to be bolted to the case) protruding radially outward.

  The case 70 forms a case oil passage 35 (see FIGS. 2 and 8) between the case 70 and the holding ring 60 in the radial direction. The case 70 has an inner peripheral surface (a radially inner surface) radially opposed to the outer peripheral surface of the cylindrical portion 64 of the holding ring 60. The inner peripheral surface of the case 70 is, for example, a surface without irregularities, and forms a radially outer boundary surface 35c of the case oil passage 35 (see FIGS. 2 and 8).

  Next, the cooling water channel 95 (see FIG. 2) formed by the retaining ring 60 will be described in detail with reference to FIGS.

  The cooling water channel 95 is connected to the case water channels 942 and 944. More specifically, the upstream end of the cooling water passage 95 is connected to the case water passage 942, and the downstream end of the cooling water passage 95 is connected to the case water passage 944.

  FIG. 9 is an explanatory diagram of the case water channels 942 and 944 in the case 70, and is a cross-sectional view when the end of the motor 10 on the X2 side in the X direction is cut along a plane perpendicular to the center axis I. FIG. 9 also shows an inlet oil passage 330 up to the oil inlet 35 a of the case oil passage 35. The inlet oil passage 330 forms the oil passage 33 (see FIG. 2). FIG. 9 also shows an outlet oil passage 360 connected to the oil outlet hole 62c. The outlet oil passage 360 forms the oil passage 36 (see FIG. 2). FIG. 9 also shows an oil passage 754 to which lubricating oil such as a bearing is supplied.

  The case water channels 942 and 944 are formed in the case 70 and extend radially inward from the outer peripheral surface of the case 70 to a position short of the bolt hole 70b for the bolt BT. The case water channels 942 and 944 extend in the X direction from near the radially inner end to the X direction X1 side (see FIG. 13 for the case water channel 942). The case water channel 942 is a flow channel connected to the discharge side of the water pump 90, and the case water channel 944 is a flow channel connected to the suction side of the water pump 90. The case channels 942 and 944 are connected to an inlet channel 951 and an outlet channel 952, respectively, at ends on the X1 side in the X direction.

  The cooling channel 95 includes a meandering channel 950, an inlet channel 951, and an outlet channel 952.

  FIG. 10 is an explanatory diagram of the inlet water channel 951 and the outlet water channel 952. The end of the motor 10 on the X2 side (X1 side than the cross section shown in FIG. 9) is cut along a plane perpendicular to the center axis I. FIG. In FIG. 10, the oil outlet hole 62c is indicated by a dashed line to indicate the position of the oil outlet hole 62c, and the highest position (level) of oil accumulated in the oil sump space is indicated by a line Lv1 for reference. I have.

  The inlet water channel 951 and the outlet water channel 952 are formed by hollow portions (cavities) in the bottom surface portion 62 of the holding ring 60. The inlet water passage 951 and the outlet water passage 952 are provided corresponding to the cooling water inlet 62d and the cooling water outlet 62e (see FIG. 5). The inlet water channel 951 and the outlet water channel 952 extend in the radial direction and the circumferential direction, respectively. That is, the inlet water passage 951 extends radially and circumferentially at the bottom surface 62 of the retaining ring 60 in a manner continuous with the cooling water inlet 62d in the X direction. The outlet water channel 952 extends in the radial direction and the circumferential direction at the bottom surface portion 62 of the holding ring 60 so as to be continuous with the cooling water outlet portion 62e in the X direction. The inlet water channel 951 and the outlet water channel 952 each extend to near the radially outer edge of the bottom surface portion 62 and continue to a meandering water channel 950 (described later).

  The inlet water channel 951 and the outlet water channel 952 are preferably formed so as to at least partially overlap with the oil sump space as viewed in the X direction, and more preferably, as shown in FIG. It is formed so as to substantially entirely overlap the storage space. For example, the inlet channel 951 and the outlet channel 952 are located below the center axis I of the stator core 112 and overlap the stator core 112 when viewed in the X direction. In this case, heat exchange between the oil accumulated in the oil sump space and the cooling water in the inlet water passage 951 and the outlet water passage 952 is efficiently realized, and the oil accumulated in the oil sump space can be efficiently cooled. As described above, the oil reservoir space is a lower space in which the highest position (see line Lv1 in FIG. 10) of the radially inner space formed by the retaining ring 60 is defined by the oil outlet hole 62c. is there. In particular, it is preferable that the inlet water channel 951 be formed so as to overlap the oil reservoir space when viewed in the X direction. This is because the cooling water in the inlet water channel 951 is lower in temperature than the cooling water in the outlet water channel 952, and has a higher heat exchange capacity than the cooling water in the outlet water channel 952. Hereinafter, forming the inlet water passage 951 and the outlet water passage 952 so as to at least partially overlap the oil sump space as viewed in the X direction is also referred to as “overlap arrangement with the oil sump space as viewed in the X direction”. .

  The position of the cooling water inlet 62d on the bottom surface 62 (see FIG. 5), that is, the connection position between the inlet water passage 951 and the cooling water inlet 62d is preferably located in the oil sump space when viewed in the X direction. They are set to overlap. Similarly, the position of the cooling water outlet 62e on the bottom surface 62, that is, the connection position between the outlet water passage 952 and the cooling water outlet 62e is preferably set so as to overlap the oil sump space when viewed in the X direction. Is done. The cooling water inlet 62d and the cooling water outlet 62e are provided at positions farther from the center axis I of the stator core 112 in the radial direction than the through hole 62b through which the bolt BT is inserted, as described above. In this case, in the bottom portion 62, the through hole 62b, the cooling water inlet portion 62d, the cooling water outlet portion 62e, and the oil outlet hole 62c are formed with the viewpoint of securing workability for fastening the bolt BT, and in the X direction view. From the viewpoint of realizing the overlap arrangement with the oil sump space and the viewpoint of forming the oil sump space whose highest position is lower than that of the rotor 10a, the arrangement can be appropriately performed from three viewpoints. In addition, the bottom portion 62 can be efficiently used to form the through hole 62b, the cooling water inlet 62d, the cooling water outlet 62e, and the oil outlet 62c. For example, in a relationship among the three members of the cooling water inlet 62d, the cooling water outlet 62e, and the oil outlet hole 62c, the cooling water inlet 62d and the cooling water outlet 62e overlap with the oil reservoir space when viewed in the X direction. As shown in FIG. 5, the oil outlet hole 62c is arranged above the cooling water outlet 62e and in the circumferential direction to the cooling water outlet 62e so as to appropriately regulate the highest position of the oil reservoir space. Are provided adjacent to each other. In a modification, the oil outlet hole 62c may be provided above the cooling water inlet 62d and adjacent to the cooling water inlet 62d in the circumferential direction.

  FIG. 11 is an explanatory view of the meandering water channel 950, and is a cross-sectional view when the end of the motor 10 on the X2 side (X1 side than the cross section shown in FIG. 10) is cut along a plane perpendicular to the central axis I. It is. FIG. 12 is a diagram schematically illustrating a deployed state of the meandering water channel 950. That is, FIG. 12 is a diagram schematically illustrating a state of the meandering water channel 950 when the cylindrical shape of the retaining ring 60 is developed into a planar shape.

  The meandering water channel 950 is formed by a hollow portion (cavity) in the cylindrical portion 64 of the holding ring 60. That is, the meandering water channel 950 is formed by the space defined by the wall surface 650 of the retaining ring 60. The wall portion 650 includes an inner diameter side wall portion 651 (an example of a first wall portion) in contact with the stator core 112, an outer diameter side wall portion 652 (an example of a second wall portion) in contact with the case oil passage 35, and an X1 side. , An end wall surface portion 654 (see FIG. 17) on the end in the X direction X2 side, and a circumferential wall surface portion 656. The wall 656 also forms side walls of concave oil passages 351, 352, and 353 described later.

  The meandering water channel 950 is formed in the cylindrical portion 64 of the holding ring 60 so as to move back and forth in the X direction. That is, the meandering water channel 950 extends from the X direction X2 side of the retaining ring 60 to the X direction X1 side, and then turns back to extend from the X direction X1 side to the X direction X2 side, and then turns back to the X direction X2 side. It extends in the circumferential direction while meandering, extending from the side to the X direction X1 side. At this time, the meandering water channel 950 is formed so that the cooling water flowing through the meandering water channel 950 can take heat from the entire stator core 112 in the X direction of the stator core 112. In the present embodiment, as an example, the meandering water channel 950 is formed so as to move back and forth over the entire holding ring 60 in the X direction, except for a range in which oil drop portions 356 and 358 described later are formed. In other words, the length of the retaining ring 60 in the X direction is determined according to the range in which the meandering channel 950 is formed in the X direction.

  More specifically, as shown in FIG. 12, the meandering water channel 950 includes a plurality of first flow channels 9501 extending in the X direction and a second flow channel 9502 extending in the circumferential direction. The meandering channel 950 is formed in such a manner that a plurality of first flow passages 9501 (12 first flow passages 9501 in the example shown in FIG. 12) are connected via a second flow passage 9502. At this time, the “meandering” is realized by alternately arranging the second flow path portions 9502 on the X1 side and the X2 side along the circumferential direction. That is, one second flow passage portion 9502 and two first flow passage portions 9501 connected to both sides (both circumferential sides) form a U-shaped flow passage, and the U-shaped flow passage is formed. The direction of the flow path is reversed in the X direction each time one second flow path portion 9502 changes one by one in the circumferential direction.

  Of the plurality of first flow path portions 9501, two first flow path portions 9501-6 and 9501-7 above the other are in the X direction from the end of the holding ring 60 on the X2 side in the X direction. Also extend to the position in front by the length L3. The range of the length L3 at the end on the X direction X2 side of the retaining ring 60 corresponds to the formation range of the oil dropping portion 356 described later. On the other hand, out of the plurality of first flow passage portions 9501, the first flow passage portions 9501 other than the first flow passage portions 9501-6 and 9501-7 are located in the X direction, and are located on the X2 side of the holding ring 60 in the X direction. It extends to a position immediately before the end (for example, the maximum position where a cavity can be formed). Thus, it is possible to maximize a region where heat exchange between the cooling water and the oil can be realized.

  Similarly, of the plurality of first flow path portions 9501, the four first flow path portions 9501-5 to 9501-8 above the other are arranged in the X direction, and are located on the X1 side of the holding ring 60 in the X direction. It extends to a position in front of the end (the end of the portion excluding the end 640, the same hereinafter) by a length L4. The range of the length L4 at the end on the X direction X1 side of the retaining ring 60 corresponds to the formation range of the oil dropping portion 358 described later. On the other hand, among the plurality of first flow passage portions 9501, the first flow passage portions 9501 other than the first flow passage portions 9501-5 to 9501-8 are in the X direction, and are located on the X1 side of the holding ring 60 in the X direction. It extends to a position immediately before the end (for example, the maximum position where a cavity can be formed). Thus, it is possible to maximize a region where heat exchange between the cooling water and the oil can be realized.

  Of the plurality of first flow path portions 9501, two first flow path portions 9501-1 and 9501-12 lower than the other (see also FIG. 11) are closest to the cooling water inlet 62d, respectively. This corresponds to the first flow passage 9501 and the first flow passage 9501 closest to the cooling water outlet 62e. That is, the concave groove 641 (and a concave oil passage 351 described later) is located between the first flow path 9501-1 and the first flow path 9501-12 in the circumferential direction. This facilitates the overlapping arrangement of the above-described inlet water passage 951 and outlet water passage 952 with the oil reservoir space as viewed in the X direction. Note that, unlike the other first flow passage portions 9501, the first flow passage portion 9501-1 and the first flow passage portion 9501-12 are formed only at one end (the end in the X direction X1 side in this example). It is not connected to the two flow path section 9502.

  In the present embodiment, the U-shaped flow path in the meandering water channel 950 is formed in a U shape (rectangular U shape) having a relatively small angle R, but the second flow path portion 9502 has a curved shape. It may be formed in a U-shape with a relatively large angle R such that Further, in a modified example, the first flow path portion 9501 may be formed so as to extend in a direction slightly inclined with respect to the X direction.

  Next, a flow of the cooling water in the cooling water passage 95 will be outlined with reference to FIGS.

  FIG. 13 is a cross-sectional view showing the relationship between the cooling water inlet 62d and the inlet water passage 951. FIG. 13 is a cross-sectional view of a part of the motor 10 viewed in a direction indicated by an arrow M1 in FIG. 10 and is a cross-sectional view when a part of the motor 10 of FIG. is there. FIG. 13 shows a case water channel 942 formed in the case 70. The case water channel 942 is connected to one end of the inlet water channel 951 via the cooling water inlet 62d. The other end of the inlet channel 951 is connected to the meandering channel 950. Although not shown, the same applies to the cooling water outlet 62e and the outlet water channel 952 side.

  FIGS. 5, 6, and 13 schematically show the flow of the cooling water in the cooling water passage 95 by dashed-dotted arrows R0 to R5.

  As shown in FIGS. 5 and 13, when the cooling water is introduced into the holding ring 60 from the cooling water inlet 62 d (see the arrow R <b> 0 in FIGS. 5 and 13), the inside of the inlet water passage 951 extends radially outward. The direction of the flow (see arrow R1 in FIGS. 6 and 13) is changed by 90 degrees (in the X direction) at the corner of the holding ring 60 (the corner formed by the bottom surface portion 62 and the cylindrical portion 64). Is introduced into the meandering water channel 950 in the cylindrical portion 64. Next, the cooling water introduced into the meandering water channel 950 of the cylindrical portion 64 flows in the circumferential direction while moving back and forth in the X direction and away from the concave groove 641 (see the arrow R2 in FIGS. 5 and 13). Thereafter, when the cooling water exceeds a half circumference in the circumferential direction, the cooling water flows in the circumferential direction in a direction approaching the concave groove 641 while moving back and forth in the X direction (see the arrow R3 in FIG. 5). Next, the direction of the flow is changed by 90 degrees (in the direction parallel to the radial direction) at the corner (the corner formed by the bottom portion 62 and the cylindrical portion 64) of the retaining ring 60, and the outlet in the bottom portion 62 is formed. Introduced into water channel 952. Next, the cooling water introduced into the bottom portion 62 flows radially inward (see arrow R4 in FIG. 6), and flows from the cooling water outlet portion 62e to the case water passage 944 (see FIG. 9) of the case 70 (see FIG. 5). Arrow R5).

  In this way, the cooling water can efficiently remove heat from the oil via the boundary surface 35b while meandering in the meandering water passage 950 of the cooling water passage 95. The cooling water can take heat from the stator core 112 while meandering in the meandering water channel 950 of the cooling water channel 95. That is, heat can be efficiently removed from the stator core 112 by flowing the cooling water through the holding ring 60 in contact with the outer peripheral surface of the stator core 112. Further, the cooling water can efficiently remove heat from the oil in the oil storage space by flowing through the inlet water passage 951. In addition, since the cooling water flowing through the outlet water channel 952 is lower in temperature than the oil in the oil sump space, heat can be taken from the oil in the oil sump space.

  Next, the case oil passage 35 will be described in detail with reference to FIGS.

  FIG. 14 is a cross-sectional view of a part of the motor 10 viewed in a direction indicated by an arrow M2 in FIG. 10 and is a cross-sectional view when a part of the motor 10 of FIG. is there.

  The upstream end of the case oil passage 35 is connected to the inlet oil passage 330. The inlet oil passage 330 is formed inside the case 70 as shown in FIGS. 9 and 14. The inlet oil passage 330 is formed in a region of the case 70 that does not overlap with the holding ring 60 in the X direction.

  The case oil passage 35 includes concave oil passages 351, 352, 353 (see FIG. 11), a cylindrical oil passage 354 (see FIG. 11), and oil dropping portions 356, 358 (described later with reference to FIG. 15 and subsequent drawings). including.

  The concave oil passages 351, 352, 353 are formed by concave grooves 641, 642, 643, respectively, as shown in FIG. 11 and FIG. The concave grooves 641, 642, 643 are as described above. The concave oil passages 351, 352, 353 are radially continuous with the cylindrical oil passage 354. The cross-sectional shape (cross-sectional shape as viewed in the X direction) of the concave oil passages 351, 352, and 353 may be constant, or the cross-sectional shape may change according to the position in the X direction.

  An end of the concave oil passage 351 on the X2 side in the X direction forms an oil inlet 35a, and is connected to the inlet oil passage 330. The concave oil passage 351 is linearly continuous in the X direction with the inlet oil passage 330 as shown in FIG. The concave oil passage 351 allows oil introduced from the inlet oil passage 330 (to be introduced toward the X direction X1 side) through the oil inlet portion 35a to efficiently spread to the X direction X1 side of the retaining ring 60. (Hereinafter, also referred to as “axial oil diffusion function”). That is, the oil introduced from the inlet oil passage 330 via the oil inlet portion 35a flows straight in the concave oil passage 351 toward the X direction X1 side, and thus the end of the holding ring 60 on the X direction X1 side. Part easily. From the viewpoint of enhancing the oil diffusion function in the axial direction, the concave oil passage 351 extends to the end 640 (see FIG. 7) of the retaining ring 60 on the X1 side in the X direction.

  Since the oil inlet 35a is formed by the end of the concave oil passage 351 on the X2 side in the X direction, the oil inlet 35a is located at a corner formed by the bottom surface 62 of the retaining ring 60 and the cylindrical portion 64. . Since the oil inlet 35a is formed by the end of the concave oil passage 351 on the X2 side in the X direction, it is located between the cooling water inlet 62d and the cooling water outlet 62e in the circumferential direction ( (See FIG. 5).

  Here, the concave oil passages 351, 352, 353 are circumferentially adjacent to the meandering water passage 950. Specifically, the first flow passage portions 9501 adjacent in the circumferential direction in the meandering water channel 950 are partitioned by the grooves 641, 642, 643 as shown in FIG. Therefore, the first flow path portion 9501 is adjacent to the concave oil passages 351, 352, 353 in the circumferential direction. In this case, since the case oil passage 35 is adjacent to the meandering water passage 950 (the first flow passage 9501) on both circumferential sides of the concave oil passages 351, 352, 353, the circumferential direction of the concave oil passages 351, 352, 353. On both sides, a good heat exchange between the cooling water and the oil is achieved. As a result, even in the concave oil passages 351, 352, and 353 that are not radially opposed to the meandering water passage 950, the oil exchanges heat with the cooling water in the meandering water passage 950, thereby increasing the overall heat exchange capability. be able to.

  In the modification, any or all of the concave oil passages 351, 352, and 353 may be omitted. That is, any or all of the grooves 641, 642, and 643 may be solid. For example, the grooves 642, 643 of the grooves 641, 642, 643 may be solid. Also in this case, since the case oil passage 35 includes the cylindrical oil passage 354 between the boundary surface 35b and the boundary surface 35c when viewed in the X direction, heat exchange between the cooling water and the oil via the boundary surface 35b is performed. Is satisfactorily realized. However, when the concave groove 641 is solid, there is a disadvantage in that the oil diffusion function in the axial direction by the concave oil passage 351 described above is reduced.

  The cylindrical oil passage 354 is an oil passage formed between the retaining ring 60 and the case 70 in the radial direction (that is, a cylindrical oil passage formed between the boundary surface 35b and the boundary surface 35c in the radial direction). Out of the oil passages 351, 352, 353 and the oil dropping parts 356, 358. Therefore, the cylindrical oil passage 354 is formed over substantially the entire outer peripheral surface of the retaining ring 60 (the entirety excluding the end 640). The cylindrical oil passage 354 may be formed such that its radial dimension is constant.

  A portion of the cylindrical oil passage 354 except for a portion that is radially continuous with the concave oil passages 351, 352, 353 and the oil dropping portions 356, 358 in the whole is radially opposed to the meandering water passage 950. That is, the oil in the cylindrical oil passage 354 and the cooling water in the meandering water passage 950 except for the oil in the concave oil passages 351, 352, 353, and the portion radially continuous with the oil dropping portions 356, 358. Only the outer diameter side wall surface portion 652 of the retaining ring 60 is interposed in the radial direction. Therefore, most of the oil in the cylindrical oil passage 354 is heated by the cooling water in the meandering water passage 950 in a direct manner (a manner in which only the outer diameter side wall surface portion 652 of the retaining ring 60 is interposed). Exchange can take place.

  15 to 18 are explanatory views of the oil dropping portions 356 and 358, FIG. 15 is a perspective view showing the upper side of the holding ring 60, and FIG. 16 passes through the oil dropping hole 3561 of the oil dropping portion 356. FIG. 17 is a cross-sectional view when cut along a plane that is perpendicular to the central axis I and is a plane that passes through the oil drop hole 3561 of the oil drop section 356 and is cut along a plane that includes the central axis I. FIG. FIG. 18 is a cross-sectional view taken along a plane that passes through the oil drop hole 3581 of the oil drop section 358 and that includes the central axis I.

  The oil dropping portions 356 and 358 are formed in the zenith region of the holding ring 60 and at a position facing the coil end 110 in the radial direction. Note that the zenith region of the retaining ring 60 indicates the highest position of the retaining ring 60 and its peripheral region. For example, the zenith region may be, for example, a range of about 60 degrees in the circumferential direction around the circumferential position corresponding to the highest position. The oil dropping portion 356 is provided for the coil end 110 on the X direction X2 side, and the oil dropping portion 358 is provided for the coil end 110 on the X direction X1 side. The oil dropping portions 356 and 358 are radially continuous with the cylindrical oil passage 354.

  The oil dropping portions 356 and 358 are configured to be recessed inward in the radial direction similarly to the grooves 641, 642 and 643, and are continuous with the grooves 642 and 643, respectively. That is, the oil dropping portion 356 extends in the circumferential direction at the end of the holding ring 60 on the X2 side in the X direction so as to be integrated with two concave grooves 642 adjacent in the circumferential direction. Further, the oil dropping portion 358 extends in the circumferential direction at the end of the holding ring 60 on the X1 side in the X direction so as to be integrated with three concave grooves 643 adjacent in the circumferential direction.

  The meandering water channel 950 is not formed in a range where the oil drop portions 356 and 358 in the retaining ring 60 are formed. That is, as shown in FIG. 15, the meandering channel 950 is formed in a range not exceeding the oil dropping portions 356 and 358 in the circumferential direction where the oil dropping portions 356 and 358 in the holding ring 60 are formed.

  An oil drop hole 3561 penetrating in the radial direction is formed in the oil drop section 356. The number of the oil dropping holes 3561 is arbitrary, but in the present embodiment, as an example, three oil dropping holes 3561 are formed. That is, as shown in FIG. 15, three oil drop holes 3561 are formed at equal intervals in the circumferential direction. The oil dropping hole 3561 is formed at the end of the oil dropping portion 356 on the X1 side. In other words, the oil dropping portion 356 is restricted to the range in which the meandering channel 950 is formed. Therefore, the oil dropping portion 356 is formed in the minimum range in the X direction in order to maximize the range in which the meandering channel 950 is formed.

  An oil drop hole 3581 penetrating in the radial direction is formed in the oil drop section 358. The number of the oil drop holes 3581 is arbitrary, but in the present embodiment, as an example, three oil drop holes 3581 are formed. That is, as shown in FIG. 15, three oil drop holes 3581 are formed at equal intervals in the circumferential direction.

  The length L3 of the oil dropping portion 356 in the X direction (see also FIG. 12) is significantly longer than the length L4 of the oil dropping portion 358 in the X direction (see also FIG. 12). The length L3 and the length L4 are determined according to the positional relationship of the stator core 112 with respect to the holding ring 60 in the X direction. Specifically, the oil dropping portions 356 and 358 are provided with the X2 side coil end 110 and the X1 side coil. An oil drop hole 3561 and an oil drop hole 3581 that are radially opposed to the end 110 are provided so as to be formed.

  Next, the flow of oil in the case oil passage 35 will be outlined with reference to FIGS. 5, 14, and 16 to 18 described above.

  5, 14, and 16 to 18 schematically show the flow of oil in the case oil passage 35 by arrows R20 to R26.

  As shown in FIG. 14, the oil is supplied from an inlet oil passage 330 (see an arrow R20 in FIG. 14), and is introduced from an oil inlet portion 35a into a concave oil passage 351 between the holding ring 60 and the case 70. . The oil introduced into the concave oil passage 351 from the oil inlet portion 35a flows straight through the concave oil passage 351 (see R21 in FIGS. 5 and 14), and enters into the radially outer cylindrical oil passage 354. (See R22 in FIG. 14). The oil introduced into the cylindrical oil passage 354 flows upward in the circumferential direction (see R23 in FIGS. 5 and 16), and reaches the oil dropping portions 356 and 358 in the zenith region (see R24 in FIG. 16). .

  Here, in the present embodiment, the case oil passage 35 (cylindrical oil passage) between the retaining ring 60 and the case 70 in the radial direction has a radial dimension over the entire length in the X direction within a predetermined range in the circumferential direction. Is substantially constant. Specifically, the case oil passage 35 extends in the circumferential direction in the radial direction over the entire length in the X direction in a range (predetermined range) excluding the formation range of the concave oil passages 351, 352, 353 and the oil dropping portions 356, 358. Are approximately constant. In this case, the circumferential flow of the oil (see R23 in FIGS. 5 and 16) is made uniform as compared with the case where the radial dimension significantly changes over the entire length in the X direction. Thus, the oil reaching the oil dropping portions 356 and 358 in the zenith region can be uniformly cooled by the cooling water.

  Further, in the present embodiment, the concave oil passage 351 into which oil is introduced from the oil inlet 35a is, as described above, the first oil passage 951 of the plurality of first flow passages 9501 that is directly connected to the inlet water passage 951. It is adjacent to the flow channel portion 9501 (the first flow channel portion 9501-1 in FIG. 12). Thus, the oil introduced into the case oil passage 35 can be cooled by the coldest cooling water in the concave oil passage 351 and then spread over the case oil passage 35. As a result, the cooling capacity of the oil in the case oil passage 35 can be efficiently increased.

  Note that, as described above with reference to FIG. 12, the first flow path portion 9501-1 and the first flow path portion 9501-12 are different from the other first flow path portions 9501 and have one end side (in this example, Only the X-direction X1 end) is connected to the second flow path portion 9502. Therefore, the concave oil passage 351 adjacent to the first flow passage 9501-1 can be formed in a manner to extend to the end in the X direction X1 side without being restricted by the second flow passage 9502. In this way, when the concave oil passage 351 is adjacent to the first flow passage portion 9501-1, the oil spread in the case oil passage 35 can be efficiently cooled, and the oil diffusion function in the axial direction described above. Can be maximized.

  The oil that has reached the oil dropping portion 356 is dropped from the oil dropping hole 3561 (see R25 in FIGS. 16 and 17), and cools the coil end 110 immediately below. Similarly, the oil that has reached the oil dropping portion 358 is dropped from the oil dropping hole 3581 (see R26 in FIG. 18), and cools the coil end 110 immediately below. The oil used for cooling the coil end 110 flows downward by gravity while traveling along the coil end 110, and accumulates in the lower portion (oil storage space) of the motor 10. The oil accumulated in the oil sump space is discharged from the oil outlet hole 62c to the outside of the motor 10 via the outlet oil passage 360 (see FIG. 9). The oil stored in the oil storage space also has a function of cooling a portion of the stator 10b that is immersed in the oil (including a part of the coil end 110).

  In this manner, the oil reaches the oil dropping portions 356 and 358 through the outer peripheral surface of the retaining ring 60 forming the meandering water channel 950 of the cooling water channel 95 (see R23 in FIGS. 5 and 16). The oil is cooled by the cooling water when passing through the outer peripheral surface of the retaining ring 60. Therefore, the cooling capacity of the oil reaching the oil dropping portions 356 and 358 is high. Since the oil having a high cooling capacity is used for cooling the coil end 110, the coil end 110 can be efficiently cooled. That is, when the oil flows in a state of contacting the outer peripheral surface of the retaining ring 60, the oil is efficiently cooled by the cooling water, and the coil end 110 can be efficiently cooled by the cooled oil.

  According to the stator cooling structure 402 according to the present embodiment described above, the following effects are particularly obtained.

  According to the stator cooling structure 402 according to the present embodiment, since the holding ring 60 forming the meandering water channel 950 is in contact with the stator core 112, only the inner diameter side wall surface portion 651 of the holding ring 60 is provided between the cooling water and the stator core 112. Only exists. Here, the cooling water is cooled by heat exchange with the outside air (for example, air passing when the vehicle is traveling) by the radiator 92 as described above, and the oil is heat-exchanged with the cooling water by the heat exchange and water cooling unit 50. Since it is cooled, the cooling water is cooler than the oil. Therefore, the stator core 112 can be cooled more efficiently by the cooling water than when another medium or member such as oil is interposed between the cooling water and the stator core 112.

  Further, according to the stator cooling structure 402 according to the present embodiment, since the retaining ring 60 forms the meandering channel 950, heat can be taken over a wide area of the stator core 112 by the cooling water flowing through the meandering channel 950. In particular, according to the stator cooling structure 402 according to the present embodiment, as described above, the meandering water passage 950 is formed so as to move back and forth over the entirety of the stator core 112 in the X direction. Can be.

  Further, according to the stator cooling structure 402 of the present embodiment, the outer peripheral surface of the retaining ring 60 functions as the boundary surface 35b of the case oil passage 35. That is, since the retaining ring 60 forming the meandering water path 950 forms the case oil path 35, only the outer diameter side wall surface portion 652 of the retaining ring 60 exists between the cooling water and the oil in the radial direction. is there. Therefore, the oil can be cooled more efficiently by the cooling water than when another member is interposed between the cooling water and the oil, for example. Therefore, according to the stator cooling structure 402, the oil cooler can be unnecessary even in the motor 10 having a relatively high output.

  Further, according to the stator cooling structure 402 according to the present embodiment, since the retaining ring 60 forms the meandering channel 950, the oil and the cooling water flowing through the meandering channel 950 in the cylindrical oil channel 354 of the case oil channel 35. The range in which heat can be exchanged between the two can be efficiently expanded. In particular, according to the stator cooling structure 402 according to the present embodiment, as described above, the meandering water channel 950 traverses the entire inner peripheral surface of the case 70 except for the region facing the oil dropping portions 356 and 358. Therefore, in the cylindrical oil passage 354 of the case oil passage 35, it is possible to maximize the range in which heat can be exchanged between the oil and the cooling water flowing through the meandering water passage 950.

  Further, by forming the meandering water channel 950, the flow direction of the cooling water can be regulated, and, for example, there is no stagnation or the like as compared with the case where the cooling water flows linearly from the cooling water inlet 62d to the cooling water outlet 62e. The range in which a significant flow rate occurs (the range in which heat exchange is substantially realized) is increased. In addition, in the case of the meandering water channel 950, random flow due to turbulence is likely to occur, and heat diffusion in the cooling water is more likely to occur. As a result, the heat exchange function and the stator core water cooling function of the heat exchange and water cooling section 50 described above can be enhanced.

  Further, according to the stator cooling structure 402 of the present embodiment, the cooling water passages (that is, the inlet water passages 951 and the outlet water passages 952) are also formed on the radially extending bottom surface portion 62 of the holding ring 60, so that the bottom surface portion is formed. Oil stored in the oil storage space of the motor 10 can be cooled more efficiently than when no cooling water passage is formed in the motor 62. That is, by the arrangement of the inlet water passage 951 and the outlet water passage 952 overlapping with the oil storage space as viewed in the X direction, the oil stored in the oil storage space can be efficiently cooled by the cooling water in the inlet water passage 951 and the outlet water passage 952. In particular, since relatively low-temperature cooling water flows through the inlet water channel 951, the inlet water channel 951 is formed on the bottom portion 62, so that the oil stored in the oil storage space of the motor 10 can be efficiently cooled.

  Further, according to the stator cooling structure 402 of the present embodiment, since the cooling water inlet 62 d and the cooling water outlet 62 e are formed on the bottom surface 62 of the holding ring 60, the cooling water is formed on the cylindrical portion 64 of the holding ring 60. The cooling capacity by the inlet water channel 951 and the outlet water channel 952 can be increased as compared with the case where the inlet portion and / or the cooling water outlet portion is formed. For example, when the cooling water inlet portion is provided in the cylindrical portion 64 of the retaining ring 60, the cooling water in the inlet water passage 951 tends to stay, so that the cooling capacity tends to deteriorate. By forming the cooling water inlet 62d and the cooling water outlet 62e on the bottom surface 62 of the holding ring 60, a cooling water inlet and / or a cooling water outlet is formed on the cylindrical portion 64 of the holding ring 60. It is also possible to minimize the physique in the radial direction as compared with the case where

  Further, according to the stator cooling structure 402 of the present embodiment, the concave oil passage 351 provided with the oil inlet portion 35a is adjacent to the meandering water passage 950 in the circumferential direction, so that the oil introduced into the case oil passage 35 is In the passage 351, cooling (heat exchange) can be performed by cooling water in the meandering water passage 950. That is, the oil introduced into the case oil passage 35 can be cooled from an early stage by utilizing heat exchange in the circumferential direction.

  In particular, the first flow path 955 adjacent to the concave oil path 351 is the first flow path 9501-1 closest to the cooling water inlet 62d among the plurality of first flow paths 9501. The cooling water in the first flow path 9501-1 closest to the cooling water inlet 62d has a lower temperature than the cooling water in the other first flow paths 9501-1. Therefore, the oil in the concave oil passage 351 is introduced from the cooling water (that is, the cooling water inlet 62d) in the first flow passage 9501-1 having the highest cooling capacity among the plurality of first flow passages 9501. With fresh cooling water).

  Further, according to the stator cooling structure 402 of the present embodiment, the concave oil passage 351 provided with the oil inlet portion 35a is located lower (that is, at the lowest position) than the other concave oil passages 352 and 353. Here, as described above, the oil introduced into the concave oil passage 351 flows linearly in the X direction in the concave oil passage 351, and the oil flows in the circumferential direction from both sides of the concave oil passage 351 in the circumferential direction. In addition, it flows upward, reaches the oil dropping portions 356 and 358 from both sides in the circumferential direction, and is dropped on the coil end 110 to be used for cooling the coil end 110. Accordingly, the time required for the oil from each side of the concave oil passage 351 to reach the upper oil dropping portions 356 and 358 in the circumferential direction is substantially the same, so that the cooling time (heat between the cooling water and the cooling water) is substantially the same. Exchange time) is approximately the same. In this way, it is possible to evenly flow the oil in the circumferential direction from both sides of the concave oil passage 351 to the oil dropping portions 356 and 358 in the circumferential direction. As a result, it is possible to equalize the cooling capacity of the oil introduced from the oil inlet portion 35a and reaching the oil dropping portions 356 and 358.

  In this embodiment, the oil in the case oil passage 35 may be constantly circulated during the operation of the motor 10 or may be circulated only during a part of the operation of the motor 10. For example, since the oil in the case oil passage 35 is mainly used for cooling the coil end 110 as described above, the oil may be circulated only during a period in which the heat generation of the coil end 110 is relatively large.

  In the above-described embodiment, the meandering water channel 950 is formed in the cylindrical portion 64 of the holding ring 60 as a preferred embodiment, but is not limited thereto. For example, a cylindrical cooling water channel may be formed in the cylindrical portion 64A of the holding ring 60A as in a holding ring 60A according to a modification shown in FIG. In this case, the retaining ring 60A has a configuration in which the concave grooves 642 and 643 are not formed and the partition wall by the concave grooves 642 and 643 does not exist in the retaining ring 60 according to the above-described embodiment. Also in this case, since the holding ring 60A forming the cylindrical cooling water passage is in contact with the stator core 112, the same effect as in the above-described embodiment can be obtained. However, in this modified example, since the cooling water flow in the cylindrical cooling water channel has a high degree of freedom, the range in which the flow velocity does not occur increases, which is more disadvantageous than the above-described embodiment. In this regard, in the present modification as well, a partition wall (partition wall such as the concave grooves 642 and 643) that regulates the flow of the cooling water may be formed, for example, so as to extend in a circumferential direction or the like.

<Stator cooling device>
Next, the stator cooling device 8 will be described in detail with reference to FIG.

  Stator cooling device 8 includes stator cooling structure 402 described above and control device 500 (an example of a cooling control device).

  Control device 500 controls stator cooling structure 402. Specifically, control device 500 controls electric oil pump 40 and water pump 90 included in stator cooling structure 402. It is assumed that control device 500 is different from the control device (not shown) of vehicle drive device 1. However, in a modified example, control device 500 may be a control device (not shown) that controls vehicle drive device 1.

  In the present embodiment, as an example, the control device 500 controls both the electric oil pump 40 and the water pump 90. However, in a modified example, the control device 500 controls the electric oil pump 40 and the water pump 90. Only the electric oil pump 40 may be controlled. In this case, the water pump 90 is controlled by another control device. In any case, the water pump 90 operates to discharge the cooling water at a constant flow rate during the cooling period, as described later.

  FIG. 20 is a diagram illustrating an example of a hardware configuration of the control device 500. FIG. 20 schematically illustrates the peripheral device 508 in association with the hardware configuration of the control device 500.

  The control device 500 includes a CPU (Central Processing Unit) 511, a RAM (Random Access Memory) 512, a ROM (Read Only Memory) 513, an auxiliary storage device 514, a drive device 515, and a communication interface 517, which are connected by a bus 519. , A wired transceiver 525 and a wireless transceiver 526 connected to the communication interface 517.

The auxiliary storage device 514 is, for example, a hard disk drive (HDD) or a solid state drive (SSD), and is a storage device that stores data related to application software and the like.
The wired transmission / reception unit 525 includes a transmission / reception unit that can communicate using a wired network. The peripheral device 508 is connected to the wired transmission / reception unit 525. However, part or all of the peripheral device 508 may be connected to the bus 519 or may be connected to the wireless transmission / reception unit 526.

  The wireless transmission / reception unit 526 is a transmission / reception unit that can communicate using a wireless network. The wireless network may include a wireless communication network of a mobile phone, the Internet, a VPN (Virtual Private Network), a WAN (Wide Area Network), and the like. In addition, the wireless transmission / reception unit 526 may include a near field communication (NFC: Near Field Communication) unit, a Bluetooth (registered trademark) communication unit, a Wi-Fi (Wireless-Fidelity) transmission / reception unit, an infrared transmission / reception unit, and the like. .

  Note that the control device 500 may be connectable to the recording medium 516. The recording medium 516 stores a predetermined program. The program stored in the recording medium 516 is installed in the auxiliary storage device 514 or the like of the control device 500 via the drive device 515. The installed predetermined program can be executed by the CPU 511 of the control device 500. For example, the recording medium 516 is a recording medium that optically, electrically or magnetically records information, such as a CD (Compact Disc) -ROM, a flexible disk, a magneto-optical disk, or the like, or an information, such as a ROM or a flash memory. May be a semiconductor memory or the like that electrically records the data.

FIG. 21 is a block diagram illustrating an example of a function related to control of stator cooling structure 402 in control device 500. FIG. 22 is an explanatory diagram of the operation area of the motor 10. In FIG. 22, the horizontal axis represents the rotation speed of the motor 10 (denoted as “motor rotation speed”), and the vertical axis represents the torque of the motor 10 (denoted as “motor torque”). Shown by curve 2200. In FIG. 22, the maximum rotation speed of the motor 10 is represented by N _max , and the maximum torque of the motor 10 is represented by τ _qmax .

  Control device 500 includes a water pump control unit 550, a rotation speed / torque information acquisition unit 552, an operating point determination unit 554, an oil pump control unit 556, and an operation area determination map storage unit 560. The water pump control unit 550, the rotation speed / torque information acquisition unit 552, the operating point determination unit 554, and the oil pump control unit 556 can be realized by the CPU 511 executing a program in a storage device (for example, the ROM 513). The operation area determination map storage unit 560 can be realized by the ROM 513.

  The water pump control unit 550 controls the water pump 90. In the present embodiment, as an example, the water pump control unit 550 operates the water pump 90 so as to discharge the cooling water at a constant flow rate during the cooling period. The cooling period may correspond to an operation period of the vehicle drive device 1. The operation period of the vehicle driving device 1 corresponds to, for example, a period in which an ignition switch (or a power supply) of the vehicle is in an ON state.

  The rotation speed / torque information obtaining unit 552 obtains rotation speed information and torque information of the motor 10. The rotation speed information can be acquired, for example, from a sensor (not shown, one element of the peripheral device 508) such as a resolver that detects the rotation speed of the motor 10. The torque information may be information indicating a torque command value generated by a control device (not shown, one element of the peripheral device 508) that controls the motor 10, or other information from which the torque of the motor 10 can be derived. It may be.

  The operating point determining unit 554 determines an operating point of the motor 10 in the operating area. The operation region of the motor 10 is, for example, a region represented by the rotation speed of the motor 10 and the torque of the motor 10 as shown in FIG. The operating point determination unit 554 acquires the rotation speed information and the torque information of the motor 10 and can determine the operating point in the operation region of the motor 10 based on the rotation speed information and the torque information.

  In the present embodiment, as an example, the operating point determination unit 554 determines that the operating point is an area A (an example of a first operating area) (see FIG. 22) and an area B (a second operating area) in the operating area of the motor 10. One example of the area) (see FIG. 22) and the area C are determined.

The region A is a region where the torque τ of the motor 10 is equal to or greater than a predetermined torque threshold τ ₁ (an example of a first threshold). Torque threshold tau ₁ will be described later. In FIG. 22, the rotation speed N ₁ indicates a rotation speed corresponding to the torque threshold τ ₁ on the curve 2200.

Region B is a region larger than the rotational speed threshold speed is predetermined for small and the motor 10 than the torque tau torque threshold tau ₁ of the motor 10 N _{2 (an} example of the second threshold value). In this embodiment, as an example, the rotation speed threshold value N ₂ is the same as the rotational speed N _1. In a variant, the rotation speed threshold value N ₂ may be significantly greater than the rotational speed N _1.

  The region C is a region different from both the region A and the region B.

  Such a region A mainly includes a region where copper loss is dominant, and a region B mainly includes a region where iron loss is dominant. The copper loss is due to heat generated in the coil electric resistance due to the flowing current, and increases in proportion to the square of the flowing current. The copper loss dominating region is a region where the flowing current is large, that is, a region where the rotation speed of the motor 10 is relatively low and the torque output by the motor 10 is relatively high. Iron loss includes hysteresis loss and eddy current loss, and both increase as the rotation speed of the motor 10 increases. Therefore, the iron loss dominating region is a region where the rotation speed of the motor 10 is relatively high.

  The oil pump controller 556 controls the electric oil pump 40 based on the operating point determined by the operating point determiner 554. Specifically, when the operating point belongs to the region A (an example of the first operating region) (see FIG. 22), the oil pump control unit 556 sets the electric oil pump 40 to the operating state and sets the operating point to the region B (Example of the second operation area) (see FIG. 22), the electric oil pump 40 is set in the non-operation state. The non-operating state is a state in which the electric oil pump 40 is not operating and a state in which the discharge amount of the electric oil pump 40 is zero. When the operating point belongs to the region C (see FIG. 22), the oil pump control unit 556 may set the electric oil pump 40 to the operating state. The point may be set smaller than when the point belongs to the area A.

  In the region A, since the electric oil pump 40 is in the operating state, the cooling water flowing through the cooling water passage 95 cools both the oil flowing through the case oil passage 35 and the stator core 112.

  Here, between the case where the oil flows in the case oil passage 35 and the case where the oil does not flow in the case oil passage 35, the case where the oil flows in the case oil passage 35 is better. The amount of heat exchange between oil and cooling water increases. This is because when the oil is flowing in the case oil passage 35, oil having a temperature difference from the cooling water is newly introduced into the case oil passage 35. In other words, when the oil is flowing in the case oil passage 35 and when the oil is not flowing in the case oil passage 35, the case where the oil is flowing in the case oil passage 35 is better. The cooling capacity of the stator core 112 by the cooling water in the cooling water passage 95 is low.

Accordingly, the torque threshold τ _1, which is a parameter that bounds the region A, is determined based on the viewpoint of preventing the region A from spreading to the operation region where the cooling of the stator core 112 is highly necessary, and the energy generated by unnecessary operation of the electric oil pump 40. May be determined from the viewpoint of reducing waste.

  In the region B, since the electric oil pump 40 is in a non-operating state, the cooling water cools both the oil stagnating in the case oil passage 35 and the stator core 112.

  As described above, the case where the oil is flowing in the case oil passage 35 and the case where the oil is not flowing in the case oil passage 35 are the cases where the oil is not flowing in the case oil passage 35. The cooling ability of the stator core 112 by the cooling water in the cooling water passage 95 is higher. When the oil stays in the case oil passage 35, the temperature difference between the oil in the case oil passage 35 and the cooling water is substantially eliminated, and the temperature of the cooling water is less likely to decrease due to heat exchange with the oil. That's why.

Thus, the rotational speed threshold value N ₂ is a parameter that bound the region B may be determined from the viewpoint of allowing cool the stator core 112 with high efficiency in the operation region is high need for cooling of the stator core 112.

  The operation area determination map storage unit 560 stores an operation area determination map. The operation area determination map represents each area when the operation area of the motor 10 shown in FIG. 22 is divided into a plurality of areas (here, three areas A, B, and C). In this case, the operation point determination unit 554 can determine the operation point with reference to the operation area determination map.

  As described above, according to the stator cooling device 8 of the present embodiment, it is possible to improve the efficiency of the lubrication / cooling system 3 that realizes cooling of the coil (particularly, the coil end 110) by oil and cooling of the stator core 112 by cooling water. It is possible.

  More specifically, in region B, electric oil pump 40 is deactivated, so that electric power for operation of electric oil pump 40 can be omitted, and cooling of stator core 112 by cooling water flowing through cooling water passage 95 can be performed. You can improve your ability. Thereby, the stator core 112 can be efficiently cooled. In particular, since the region B mainly includes the iron loss dominant region as described above, the stator core 112 can be efficiently cooled in an operation region where cooling of the stator core 112 is highly required.

  In the region A, the electric oil pump 40 is in the operating state, so that the coil end 110 can be efficiently cooled by the oil cooled by the heat exchange with the cooling water flowing through the cooling water passage 95 as described above. . In particular, since the region A mainly includes the copper loss dominant region as described above, the coil end 110 can be efficiently cooled in an operation region where cooling of the coil end 110 is highly required.

  Next, an operation example of the control device 500 will be described.

  FIG. 23 is a flowchart illustrating an example of a process performed by control device 500. In the subsequent processing flow diagrams (flow charts), the processing order of each step may be changed as long as the relationship between the input and output of each step is not impaired.

  In step S230, control device 500 determines whether or not the cooling start condition has been satisfied. The cooling start condition is arbitrary, but may be satisfied, for example, when the ignition switch is turned on. If the determination is "YES", the flow proceeds to step S231; otherwise, the flow ends.

  In step S231, the control device 500 brings the water pump 90 into an operating state.

  In step S232, control device 500 obtains rotation speed information and torque information of motor 10.

  In step S233, control device 500 determines whether or not the current operating point is within region B based on the rotation speed information and the torque information obtained in step S232. If the determination is "YES", the flow proceeds to step S234; otherwise, the flow proceeds to step S235.

  In step S234, control device 500 brings electric oil pump 40 into a non-operating state. In this case, the amount of oil discharged from the electric oil pump 40 is 0 [L / min].

  In step S235, control device 500 determines whether or not the current operating point is within region C based on the rotation speed information and the torque information obtained in step S232. If the result of the determination is "YES", the flow proceeds to step S236; otherwise (i.e., if the current operating point is within the area A), the flow proceeds to step S237.

  In step S236, control device 500 sets electric oil pump 40 to an operating state. At this time, the control device 500 controls the electric oil pump 40 so that the amount of oil discharged from the electric oil pump 40 becomes a predetermined amount Q1 [L / min]. The predetermined amount Q1 may be, for example, about half of a predetermined amount Q2 described later.

  In step S237, control device 500 sets electric oil pump 40 to an operating state. At this time, the control device 500 controls the electric oil pump 40 so that the amount of oil discharged from the electric oil pump 40 becomes a predetermined amount Q2 [L / min]. The predetermined amount Q2 may correspond to, for example, the maximum ejection amount.

  In step S238, control device 500 determines whether or not the cooling end condition has been satisfied. The cooling end condition is arbitrary, but may be satisfied when, for example, the ignition switch is turned off. If the determination is "YES", the flow proceeds to step S239. Otherwise, the flow returns to step S231, and the processing from step S231 is repeated.

  In step S239, the control device 500 sets the water pump 90 and the electric oil pump 40 to a non-operating state. In this case, control device 500 stops the operation of electric oil pump 40 when electric oil pump 40 is in the operating state.

  According to the processing shown in FIG. 23, in the region A, the electric oil pump 40 is set in the operating state, and the amount of oil discharged from the electric oil pump 40 is set to the predetermined amount Q2 [L / min]. Thereby, in the region A, the coil end 110 can be efficiently cooled. In the area B, the electric oil pump 40 is in a non-operating state. Thus, in region B, stator core 112 can be efficiently cooled. Further, in the region C, the electric oil pump 40 is in the operating state, and the amount of oil discharged from the electric oil pump 40 is set to a predetermined amount Q1 [L / min]. Thereby, in region C, both stator core 112 and coil end 110 can be cooled.

  Next, a stator cooling device according to another embodiment will be described with reference to FIG.

  The stator cooling device according to the other embodiment is different from the stator cooling device 8 according to the above-described embodiment in that the control device 500 is replaced with a control device 500A. In the following, components that may be the same as those of the stator cooling device 8 according to the above-described embodiment will be given the same reference numerals, and descriptions thereof may be omitted.

  FIG. 24 is a block diagram illustrating an example of a function related to control of stator cooling structure 402 in control device 500A. The hardware configuration of control device 500A may be the same as the configuration shown in FIG. FIG. 25 is an explanatory diagram of an operation line (a contour line related to a flowing current). In FIG. 25, the horizontal axis represents the rotation speed of the motor 10 (denoted by “motor rotation speed”), the vertical axis represents the torque of the motor 10 (denoted by “motor torque”), and the maximum output characteristic of the motor 10 is represented by a curve. 2200.

  The control device 500A is different from the control device 500 according to the above-described embodiment in that the operation point determination unit 554 and the operation area determination map storage unit 560 are omitted, and the rotation speed / torque information acquisition unit 552 and the oil pump control unit 556 The difference is that the energization current information acquisition unit 552A and the oil pump control unit 556A are replaced with each other. The energizing current information acquisition unit 552A and the oil pump control unit 556A can be realized by the CPU 511 executing a program in a storage device (for example, the ROM 513).

  The energizing current information acquiring unit 552A acquires energizing current information indicating the magnitude of the current (energizing current) flowing through the motor 10 (hereinafter, referred to as “energizing current value”). The energizing current information can be acquired from, for example, a current sensor (not shown, one element of the peripheral device 508) that detects the magnitude of the energizing current of the motor 10. The energization current information may be, for example, information relating to a specific phase of each phase of the motor 10 or information relating to all phases. The energizing current information may be information indicating an energizing current command value generated by a control device (not shown, one element of the peripheral device 508) that controls the motor 10, or the energizing current value of the motor 10 can be derived. Other information may be used.

  The oil pump control unit 556A controls the electric oil pump 40 based on the energization current information acquired by the energization current information acquisition unit 552A. Specifically, when the energizing current value is equal to or greater than a predetermined first current value, the oil pump control unit 556A sets the electric oil pump 40 into an operating state and sets the energizing current value to a predetermined second current value. When the current value is smaller than the current value, the electric oil pump 40 is set to the non-operation state. Note that the comparison of the energizing current values may be realized based on the effective value, the maximum value (for example, the maximum value within the latest predetermined period), or the like.

  The region where the energizing current value is equal to or larger than the predetermined first current value corresponds to region A1 shown in FIG. 25 and mainly includes the copper loss dominant region. In FIG. 25, the contour line related to the first current value is indicated by reference numeral 2501. The region where the energizing current value is smaller than the second current value that is predetermined corresponds to region B1 shown in FIG. 25 and includes the iron loss dominating region. In FIG. 25, the contour line related to the second current value is indicated by reference numeral 2502.

  In the area A <b> 1, the electric oil pump 40 is in the operating state, so the cooling water cools both the oil flowing in the case oil passage 35 and the stator core 112.

  Here, the oil flows in the case oil passage 35 between the case where the oil flows in the case oil passage 35 and the case where the oil does not flow in the case oil passage 35 as described above. In the case, the cooling ability of the stator core 112 by the cooling water in the cooling water passage 95 is lower.

  Therefore, the first current value, which is a parameter that bounds the region A1, is determined based on the viewpoint of preventing the region A1 from spreading to the operation region where the cooling of the stator core 112 is highly necessary, and the energy generated by unnecessary operation of the electric oil pump 40. May be determined from the viewpoint of reducing waste. The area A1 is determined to include at least a part of the area A described above, and may be determined to include the area A described above.

  In the region B <b> 1, the electric oil pump 40 is in a non-operating state, so that the cooling water mainly cools the stator core 112 of the oil stagnating in the case oil passage 35 and the stator core 112.

  As described above, the case where the oil is flowing in the case oil passage 35 and the case where the oil is not flowing in the case oil passage 35 are the cases where the oil is not flowing in the case oil passage 35. The cooling ability of the stator core 112 by the cooling water in the cooling water passage 95 is higher.

  Therefore, the second current value, which is a parameter that bounds the region B1, may be determined from the viewpoint of allowing the stator core 112 to be cooled with high efficiency in an operation region where the need for cooling the stator core 112 is high. The area B1 is determined to include a part of the area B described above. Note that the second current value is equal to or less than the first current value, and may be the same as the first current value. When the second current value is the same as the first current value, the configuration is such that the region C1 in FIG. 25 does not exist.

  As described above, according to the stator cooling device of the present embodiment, it is possible to improve the efficiency of the lubrication / cooling system 3 that realizes cooling of the coil (particularly, the coil end 110) by oil and cooling of the stator core 112 by cooling water. It is.

  Specifically, in the region B1, the electric oil pump 40 is deactivated, so that electric power for the operation of the electric oil pump 40 can be omitted, and cooling of the stator core 112 by the cooling water flowing through the cooling water passage 95 can be performed. You can improve your ability. Thereby, the stator core 112 can be efficiently cooled. In particular, since the region B1 includes the iron loss dominating region as described above, the stator core 112 can be efficiently cooled in an operation region in which the need for cooling the stator core 112 is high.

  In the region A1, the electric oil pump 40 is in the operating state, so that the coil end 110 can be efficiently cooled by the oil cooled by the heat exchange with the cooling water flowing through the cooling water passage 95 as described above. . In particular, since the region A1 mainly includes the copper loss dominant region as described above, the coil end 110 can be efficiently cooled in an operation region where the cooling of the coil end 110 is highly necessary.

  FIG. 26 is a flowchart illustrating an example of a process performed by control device 500A.

  In step S260, control device 500A determines whether a cooling start condition has been satisfied. If the determination is "YES", the flow proceeds to step S261; otherwise, the flow ends.

  In step S261, control device 500A causes water pump 90 to operate.

  In step S262, control device 500A acquires energizing current information of motor 10.

  In step S263, control device 500A determines whether or not the current operating point is within region B1, based on the supplied current information obtained in step S262. If the determination is "YES", the flow proceeds to step S264; otherwise, the flow proceeds to step S265.

  In step S264, control device 500A brings electric oil pump 40 into a non-operating state. In this case, the amount of oil discharged from the electric oil pump 40 is 0 [L / min].

  In step S265, control device 500A determines whether or not the current operating point is within region C1, based on the energized current information obtained in step S262. If the result of the determination is "YES", the flow proceeds to step S266; otherwise (i.e., if the current operating point is within the area A1), the flow proceeds to step S267.

  In step S266, control device 500A brings electric oil pump 40 into an operating state. At this time, the control device 500A controls the electric oil pump 40 so that the amount of oil discharged from the electric oil pump 40 becomes a predetermined amount Q1 [L / min]. Note that the predetermined amount Q1 may be zero.

  In step S267, control device 500A causes electric oil pump 40 to operate. At this time, the control device 500A controls the electric oil pump 40 so that the amount of oil discharged from the electric oil pump 40 becomes a predetermined amount Q2 [L / min].

  In step S268, control device 500A determines whether or not the cooling end condition has been satisfied. If the determination is "YES", the flow proceeds to step S269. Otherwise, the flow returns to step S261 to repeat the processing from step S261.

  In step S269, control device 500A causes water pump 90 and electric oil pump 40 to be in an inactive state. In this case, control device 500A stops the operation of electric oil pump 40 when electric oil pump 40 is in the operating state.

  According to the processing shown in FIG. 26, in the area A1, the electric oil pump 40 is set to the operating state, and the amount of oil discharged from the electric oil pump 40 is set to the predetermined amount Q2 [L / min]. Thereby, in the area A1, the coil end 110 can be efficiently cooled. In the region B1, the electric oil pump 40 is in a non-operating state. Thus, in region B1, stator core 112 can be efficiently cooled. Further, in the region C1, the electric oil pump 40 is in the operating state, and the amount of oil discharged from the electric oil pump 40 is set to a predetermined amount Q1 [L / min]. Thereby, in region C1, both stator core 112 and coil end 110 can be cooled.

  In the stator cooling device according to the other embodiment described above with reference to FIG. 24 and subsequent figures, as shown in FIG. 25, the region A1 (the same applies to the region C1) extends to the iron loss dominant region. In a part of the iron loss control region, the electric oil pump 40 is in an operating state. In other words, in the stator cooling device according to the other embodiment, the electric oil pump 40 can be made inoperative only in a part of the iron loss dominating region.

In this regard, in order to prevent such inconvenience, rotation speed information and torque information of the motor 10 may be used. For example, area A1, energization current value is a first current value or more, the rotation speed of the motor 10 may be limited to the region is less than the rotational speed N _{1 (above).} Further, the area A1 may be limited to an area where the energizing current value is equal to or greater than the first current value and the torque of the motor 10 is equal to or greater than the torque threshold τ ₁ (described above).

  In consideration of the fact that the energizing current value increases due to the field weakening control in the high rotation region of the motor 10, the electric oil pump 40 is operated during the field weakening control even if the operating point belongs to the region A1. May not be performed.

  In the other embodiment described above with reference to FIG. 24 and subsequent figures, the oil pump control unit 556A controls the electric oil pump 40 based on the relationship and the energized current value shown in FIG. 25. Not limited. The oil pump control unit 556A determines the operating point based on the torque of the motor 10 and the number of rotations of the motor 10 in each of the operating regions shown in FIG. 25, similarly to the embodiment described above with reference to FIGS. It may be determined which of A1, B1, and C1 it belongs to. In this case, the contour lines 2501 and 2502 function as a map (an example of stored information) indicating the first torque threshold and the second torque threshold corresponding to each rotation speed. That is, the oil pump control unit 556A performs the first map (contour line 2501) defining the first relationship between the rotation speed and the first torque threshold, and the second map defining the second relationship between the rotation speed and the second torque threshold. Based on the (contour line 2502), the rotation speed of the motor 10 and the torque of the motor 10, it is determined which of the operation areas A1, B1, and C1 shown in FIG. Then, the oil pump control unit 556A determines that the torque of the motor 10 is equal to or greater than a first torque threshold (torque value on the contour line 2501) corresponding to the rotation speed of the motor 10 (that is, the operating point belongs to the area A1). Then, when the electric oil pump 40 is in the operating state and the torque of the motor 10 is less than the second torque threshold (the torque value on the contour line 2502) corresponding to the rotation speed of the motor 10 (that is, the operating point is in the region B1). ), The electric oil pump 40 may be in a non-operating state. The oil pump control unit 556 </ b> A determines that the torque of the motor 10 is equal to or more than a second torque threshold value (torque value on the contour line 2502) corresponding to the rotation speed of the motor 10 and a first torque threshold value (corresponding to the rotation speed of the motor 10). If it is less than the torque value on the contour line 2501 (that is, if the operating point belongs to the region C1), the electric oil pump 40 is set to the operating state, and the amount of oil discharged from the electric oil pump 40 is reduced by a predetermined amount. Q1 [L / min] may be used.

  As described above, each embodiment has been described in detail. However, the present invention is not limited to a specific embodiment, and various modifications and changes can be made within the scope described in the claims. It is also possible to combine all or a plurality of the components of the above-described embodiment.

  For example, in the above-described embodiment, in the operating state of the water pump 90, the non-operating state of the electric oil pump 40 is realized under specific conditions, but is not limited thereto. For example, instead of the non-operating state of the electric oil pump 40, a state in which the electric oil pump 40 is operating but the discharge amount is substantially zero, or a state in which the electric oil pump 40 is operating is discharged. A state in which the amount is significantly less than in the normal operating state may be achieved. In the above description, the operating state of the electric oil pump 40 means a normal operating state. For example, if the discharge amount (or the lower limit of the variable range when the discharge amount is variable) in the operation state (normal operation state) of the electric oil pump 40 is Q1, the discharge amount is in the normal operation state. The state that is significantly less than that corresponds to a state in which the ejection amount is significantly less than Q1.

  In the above-described embodiment, the cooling water inlet 62d and the cooling water outlet 62e are formed on the bottom surface 62 of the holding ring 60, but the invention is not limited to this. For example, only the cooling water inlet 62d of the cooling water inlet 62d and the cooling water outlet 62e may be formed on the bottom surface 62 of the holding ring 60. In this case, the cooling water outlet 62 e is formed on the cylindrical portion 64 of the holding ring 60 in a manner to be radially connected to the end of the meandering water channel 950 on the X2 side of the first flow path 9501-12. Frequently, outlet channel 952 may be omitted. Similarly, in another modification, the cooling water inlet 62d and the cooling water outlet 62e are formed in the cylindrical portion 64 of the holding ring 60, and the inlet water channel 951 and the outlet water channel 952 may be omitted.

  Further, the cooling water inlet 62d and the cooling water outlet 62e are provided on the bottom surface 62 of the holding ring 60 so as to be adjacent to each other in the circumferential direction, but are not limited thereto. For example, the cooling water inlet portion 62d and the cooling water outlet portion 62e may be provided on the bottom surface portion 62 of the holding ring 60 at an offset of, for example, 40 degrees or more in the circumferential direction. The cooling water inlet 62d and the cooling water outlet 62e may be provided on the bottom surface 62 of the holding ring 60 so as to be offset in the circumferential direction and the radial direction.

  Further, in the above-described embodiment, as a preferred embodiment, the concave oil passage 351 forming the oil inlet 35 a is configured such that the lowest-temperature cooling water of the plurality of first flow passages 9501 forming the meandering water passage 950 is used. It is adjacent to, but not limited to, the first passage 9501-1 that passes through (ie, the first passage 9501-1 directly connected to the inlet water passage 951). For example, the concave oil passage 351 forming the oil inlet portion 35a may not be adjacent to the first flow passage portion 9501-1 in the circumferential direction, but may be adjacent to another first flow passage portion 9501 in the circumferential direction. In this case, the effect of the case where the concave oil passage 351 is adjacent to the first flow passage portion 9501-1 (that is, the oil spread in the case oil passage 35 can be efficiently cooled, and the above-described axial oil diffusion The effect of maximizing the function) cannot be obtained, but the other effects of the above-described embodiment are still obtained.

  The case oil passage 35 (cylindrical oil passage) between the retaining ring 60 and the case 70 in the radial direction is provided in a predetermined range in the circumferential direction (concave oil passages 351, 352, 353, and oil dropping portions 356, 358). In the range excluding the formation range of), the radial dimension is substantially constant over the entire length in the X direction, but is not limited thereto. For example, the case oil passage 35 may have irregularities, steps, or the like in a range other than the formation range of the concave oil passages 351, 352, 353 and the oil dropping portions 356, 358.

  Further, in the above-described embodiment, the concave oil passage 351 and the first flow passages 9501-1 and 9501-12 are arranged in the lowermost region, but are not limited thereto. The concave oil passage 351 and the first flow paths 9501-1 and 9501-12 may be provided in such a manner that the concave oil passage 352 or the concave oil passage 353 is formed below the concave oil passage 351.

  In the above-described embodiment, the concave oil passage 351 extends in the X direction with a substantially equal cross section (a cross section viewed in the X direction), and the extreme end on the X2 side forms the oil inlet 35a. The oil inlet portion 35a is formed at a corner formed by the bottom portion 62 and the cylindrical portion 64, but is not limited to this. For example, the concave oil passage 351 may be bent radially inward at the end on the X2 side in the X direction, and the oil inlet 35 a may be formed in the bottom surface 62.

  In the above-described embodiment, the case oil passage 35 has the cylindrical oil passage 354 that radially opposes the meandering water passage 950, but is not limited thereto. For example, the case oil passage 35 does not have the cylindrical oil passage 354, and may be in the form of a meandering oil passage arranged in parallel with the meandering water passage. In this case, the meandering oil passage may be provided in such a manner as to be circumferentially adjacent to the meandering waterway. In this case, the meandering oil passage may be formed so as not to intersect with the meandering waterway, or may be formed so as to intersect. In the case of the intersecting mode, in the intersection area, the meandering oil passage and the meandering waterway may be reduced in thickness in the radial direction, so that an increase in the thickness in the intersection area may be suppressed.

<Appendix>
It should be noted that the following supplementary notes are further disclosed with respect to the above embodiments. In addition, among the effects described below, the effects according to each additional mode with respect to one mode are additional effects due to the additional modes.

One mode includes an electric oil pump (40), an oil circulation unit (400) that circulates oil that can cool a coil of the rotating electric machine (10),
Including a water pump (90), a first wall portion (651) in contact with a stator core (112) of the rotating electric machine (10) and a second wall portion (652) in contact with an oil passage (35) through which the oil passes. A cooling water circulating unit (401) for circulating cooling water through a cooling water passage (95) formed by the wall surface;
In the operating state of the water pump (90), in at least a part of the first operation region (A) where the torque of the rotating electric machine (10) is equal to or greater than a predetermined first threshold (τ ₁ ), The oil pump (40) is operated, the torque of the rotating electric machine (10) is smaller than the first threshold value (τ ₁ ), and the rotation speed of the rotating electric machine (10) is set to a predetermined second threshold value (N ₂ ) At least a part of the second operation region (B) larger than the operation region (B) includes a pump cooling device (500) for reducing a discharge amount of the electric oil pump (40) in the operation state. Device (8).

According to the present embodiment, in at least a part of the first operation region (A), the electric oil pump (40) is operated together with the water pump (90), so that the electric oil pump (40) is circulated by the electric oil pump (40). The oil reaching the oil passage (35) can be efficiently cooled by the cooling water in the cooling water passage (95), and the coil of the rotating electric machine (10) can be efficiently cooled using the cooled oil. That is, the coil of the rotating electric machine (10) can be continuously cooled by the cooled oil while the circulating new oil is cooled by the cooling water. The first operation region (A) is a region where the torque of the rotating electric machine (10) is equal to or more than the first threshold value (τ ₁ ) and mainly includes the copper loss dominating region. The effect can be expected. Further, in at least a part of the second operation region (B), the discharge amount of the electric oil pump (40) is smaller than that in the operating state, so that the discharge amount of the electric oil pump (40) is relatively large. The power consumption of the electric oil pump (40) can be reduced as compared with the case of the operating state, and the ability of the cooling water in the cooling water passage (95) to cool the stator core (112) can be increased. In the second operation region (B), the torque of the rotating electric machine (10) is smaller than the first threshold value (τ ₁ ) and the rotation speed of the rotating electric machine (10) is larger than a predetermined second threshold value (N ₂ ). Since this is a large area and mainly includes the iron loss dominating area, a cooling effect on the stator core (112) can be expected in the iron loss dominating area.

In the present embodiment, the cooling water passage (95) is formed inside a cylindrical cooling water passage forming member (60, 60A), and the cooling water passage forming member (60, 60A) is connected to the rotating electric machine (10). ), The first wall surface portion (651) in contact with the outer peripheral surface of the stator core (112) inside in the radial direction, and the second wall surface portion (652) outside in the radial direction.
The oil passage (35) may be formed between the case (70) of the rotating electric machine (10) and the cooling water passage forming member (60, 60A) in a radial direction of the rotating electric machine (10).

  In this case, the cooling water channel (95) can be formed inside the cooling water channel forming member (60, 60A), and the cooling water in the cooling water channel forming member (60, 60A) passes only through the first wall surface portion (651). The stator core (112) can be cooled, and can exchange heat with oil only through the second wall portion (652).

  In the present embodiment, the oil circulation section (400) does not include an oil cooler.

  In this case, the required cooling performance for the oil can be ensured while reducing the cost by eliminating the oil cooler.

  Further, in the present embodiment, the pump control device (500) operates the electric oil pump (40) in the first operation region (A) based on the rotation speed and the torque of the rotating electric machine (10). And the electric oil pump (40) may be in a non-operating state in the second operation region (B).

  In this case, the electric oil pump (40) can be switched between an operating state and a non-operating state using information representing the number of revolutions and torque of the rotating electric machine (10). Further, since the electric oil pump (40) is in the operating state in the first operation area (A), the coil of the rotating electric machine (10) can be efficiently cooled mainly in the copper loss dominant area. Further, since the electric oil pump (40) is in the non-operation state in the second operation area (B), the stator core (112) can be efficiently cooled while suppressing power consumption mainly in the iron loss dominant area.

Another form includes an oil circulating unit (400) that includes an electric oil pump (40) and circulates oil that can cool a coil of the rotating electric machine (10).
Including a water pump (90), a first wall portion (651) in contact with a stator core (112) of the rotating electric machine (10) and a second wall portion (652) in contact with an oil passage (35) through which the oil passes. A cooling water circulating unit (401) for circulating cooling water through a cooling water passage (95) formed by the wall surface;
In the operating state of the water pump (90), when the magnitude of the current is equal to or greater than a predetermined first current value based on the magnitude of the current flowing through the rotating electric machine (10), When the oil pump (40) is operated and the magnitude of the current is smaller than a second current value that is a predetermined second current value and is equal to or less than the first current value, the electric oil pump is operated. (40) A stator cooling device including: a pump control device (500) for reducing a discharge amount in the operating state.

  According to the present embodiment, the information indicating the current flowing through the rotating electric machine (10) is used to operate the electric oil pump (40) and reduce the discharge amount of the electric oil pump (40) as compared with the operation state. (For example, a non-operating state). The operating point when the magnitude of the current is equal to or larger than the first current value is included in at least a part of the first operation area (A), and the operation when the magnitude of the current is smaller than the second current value is performed. The point is included in a part of the second operation area (B). Thus, the coil of the rotating electric machine (10) can be efficiently cooled mainly in the copper loss dominant region, and the stator core (112) can be efficiently cooled while suppressing power consumption mainly in the iron loss dominant region.

Another form includes an oil circulating unit (400) that includes an electric oil pump (40) and circulates oil that can cool a coil of the rotating electric machine (10).
Including a water pump (90), a first wall portion (651) in contact with a stator core (112) of the rotating electric machine (10) and a second wall portion (652) in contact with an oil passage (35) through which the oil passes. A cooling water circulating unit (401) for circulating cooling water through a cooling water passage (95) formed by the wall surface;
In an operation state of the water pump (90), storage information defining a first relationship (2501) between a rotation speed and a first torque threshold and a second relationship (2502) between a rotation speed and a second torque threshold; When the torque of the rotating electric machine (10) is equal to or greater than the first torque threshold value corresponding to the rotating speed of the rotating electric machine (10), based on the rotation speed and the torque of the rotating electric machine (10), The electric oil pump (40) is operated when the torque of the rotating electric machine (10) is less than the second torque threshold value according to the rotation speed of the rotating electric machine (40). A stator cooling device including a pump control device (500) for reducing a discharge amount in the operating state.

  According to the present embodiment, the information indicating the number of rotations and the torque of the rotating electric machine (10) is used to operate the electric oil pump (40) and to reduce the discharge amount of the electric oil pump (40) in the operating state. Switching (for example, a non-operating state). Thereby, the coil of the rotating electric machine (10) can be efficiently cooled mainly in the copper loss dominant region, and the stator core (112) can be efficiently cooled while suppressing power consumption mainly in the iron loss dominant region.

Another form is a cooling control device (500) applicable to a stator cooling structure (402) including an oil circulation part (400) and a cooling water circulation part (401),
The oil circulation unit (400) includes an electric oil pump (40), and can circulate oil that can cool a coil of the rotating electric machine (10).
The cooling water circulation unit (401) includes a water pump (90), and includes a first wall portion (651) in contact with a stator core (112) of the rotating electric machine (10) and a first wall portion (65) in contact with an oil passage (35) through which the oil passes. Cooling water can be circulated through a cooling water passage (95) formed by a wall portion including the two wall portions (652);
In the operating state of the water pump (90), in at least a part of the first operation region (A) where the torque of the rotating electric machine (10) is equal to or greater than a predetermined first threshold (τ ₁ ), With the oil pump (40) in an operating state, the torque of the rotating electric machine (10) is smaller than the first threshold value (τ ₁ ) and the number of revolutions of the rotating electric machine is greater than a predetermined second threshold value (N ₂ ). A cooling control device (500) that reduces the discharge amount of the electric oil pump (40) in at least a part of the second operation region (B) that is larger than that in the operating state.

According to the present embodiment, in at least a part of the first operation region (A), the electric oil pump (40) is operated together with the water pump (90), so that the electric oil pump (40) is circulated by the electric oil pump (40). The oil reaching the oil passage (35) can be efficiently cooled by the cooling water in the cooling water passage (95), and the coil of the rotating electric machine (10) can be efficiently cooled using the cooled oil. The first operation region (A) is a region where the torque of the rotating electric machine (10) is equal to or more than the first threshold value (τ ₁ ) and mainly includes the copper loss dominating region. The effect can be expected. Further, in at least a part of the second operation region (B), the discharge amount of the electric oil pump (40) is smaller than that in the operating state, so that the discharge amount of the electric oil pump (40) is relatively large. The power consumption of the electric oil pump (40) can be reduced as compared with the case of the operating state, and the ability of the cooling water in the cooling water passage (95) to cool the stator core (112) can be increased. In the second operation region (B), the torque of the rotating electric machine (10) is smaller than the first threshold value (τ ₁ ) and the rotation speed of the rotating electric machine (10) is larger than a predetermined second threshold value (N ₂ ). Since this is a large area and mainly includes the iron loss dominating area, a cooling effect on the stator core (112) can be expected in the iron loss dominating area.

DESCRIPTION OF SYMBOLS 1 Vehicle drive device 3 Lubrication / cooling system 8 Stator cooling device 10 Motor 10a Rotor 10b Stator 12 Reduction mechanism 14 Differential device 22 Lubrication part 23 Cooling part 30 Tank 30a Strainer 31 Oil passage 32 Oil passage 33 Oil passage 34 Oil passage 35 Case Oilway (oilway)
35a Oil inlet portion 35b Boundary surface 35c Boundary surface 36 Oil passage 40 Electric oil pump 42 Mechanical oil pump 50 Heat exchange and water cooling unit 60, 60A Retaining ring 62 Bottom part 62a Hole 62b Through hole 62c Oil outlet hole 62d Cooling water inlet Part 62e cooling water outlet part 62f bulging part 62g bulging part 64, 64A cylindrical part 70 case 90 water pump 92 radiator 94 cooling water passage 95 cooling water passage 110 coil end 112 stator core 140 ring gear 141 pinion gear 142 side gear 330 inlet oil passage 351 concave oil Passage 352 Concave oil passage 353 Concave oil passage 354 Cylindrical oil passage 356 Oil dripping unit 358 Oil dripping unit 360 Outlet oil passage 400 Oil circulation unit 401 Cooling water circulation unit 402 Stator cooling structure 550 Water pump control unit 552 Acquisition of rotation speed / torque information Part 552A Energizing current information acquisition section 554 Operating point determination section 556, 556A Oil pump control section 560 Operation area determination map storage section 640 End section 640a Seal groove 641 Concave groove 642 Concave groove 643 Concave groove 650 Wall portion 651 Inner side wall surface portion 652 Outer diameter Side wall surface portion 653 End wall surface portion 654 End wall surface portion 656 Wall surface portion 942 Case water channel 944 Case water channel 950 Meandering water channel 951 Inlet water channel 952 Outlet water channel 3561 Oil drop hole 3581 Oil drop hole 9501 First flow path portion 9502 Second flow path Part BT bolt I center axis

Claims (7)

An oil circulating unit that includes an electric oil pump and circulates oil that can cool the coil of the rotating electric machine,
The cooling water is circulated in a mode including a water pump and passing through a cooling water passage formed by a wall surface portion including a first wall surface portion in contact with a stator core of the rotating electric machine and a second wall surface portion in contact with an oil passage through which the oil passes. Cooling water circulation section,
In the operating state of the water pump, in at least a part of the first operation region in which the torque of the rotating electric machine is equal to or more than a predetermined first threshold, the electric oil pump is operated, and the torque of the rotating electric machine is reduced. In at least a part of the second operation region where the rotation speed of the rotating electric machine is smaller than the first threshold value and larger than a predetermined second threshold value, the discharge amount of the electric oil pump is set to be smaller than in the operation state. A stator cooling device, comprising: The cooling water channel is formed inside a cylindrical cooling water channel forming member, and the cooling water channel forming member radially inward of the rotating electric machine, the first wall portion contacting the outer peripheral surface of the stator core, Having the second wall portion radially outward,
The stator cooling device according to claim 1, wherein the oil passage is formed between the case of the rotating electric machine and the cooling water passage forming member in the radial direction.   The stator cooling device according to claim 1, wherein the oil circulation unit does not include an oil cooler.   The pump control device sets the electric oil pump to an operation state in the first operation region and sets the electric oil pump to a non-operation state in the second operation region based on a rotation speed and a torque of the rotary electric machine. The stator cooling device according to any one of claims 1 to 3, An oil circulating unit that includes an electric oil pump and circulates oil that can cool the coil of the rotating electric machine,
The cooling water is circulated in a mode including a water pump and passing through a cooling water passage formed by a wall surface portion including a first wall surface portion in contact with a stator core of the rotating electric machine and a second wall surface portion in contact with an oil passage through which the oil passes. Cooling water circulation section,
In the operating state of the water pump, when the magnitude of the current is equal to or greater than a predetermined first current value based on the magnitude of the current flowing through the rotating electric machine, the electric oil pump is activated. When the magnitude of the current is smaller than a second current value that is a predetermined second current value and is equal to or less than the first current value, the discharge amount of the electric oil pump is increased in the operating state. And a pump control device for reducing stator cooling. An oil circulating unit that includes an electric oil pump and circulates oil that can cool the coil of the rotating electric machine,
The cooling water is circulated in a mode including a water pump and passing through a cooling water passage formed by a wall surface portion including a first wall surface portion in contact with a stator core of the rotating electric machine and a second wall surface portion in contact with an oil passage through which the oil passes. Cooling water circulation section,
In the operating state of the water pump, stored information defining a first relationship between a rotation speed and a first torque threshold and a second relationship between a rotation speed and a second torque threshold, and a rotation speed and a torque of the rotary electric machine. When the torque of the rotating electric machine is equal to or more than the first torque threshold corresponding to the number of rotations of the rotating electric machine, the electric oil pump is operated, and the torque of the rotating electric machine is reduced to And a pump control device that, when the rotational speed is less than the second torque threshold, reduces the discharge amount of the electric oil pump in the operating state. A cooling control device applicable to a stator cooling structure including an oil circulation unit and a cooling water circulation unit,
The oil circulation unit includes an electric oil pump, and is capable of circulating oil capable of cooling a coil of the rotating electric machine,
The cooling water circulation portion includes a water pump, a cooling water passage formed by a wall surface portion including a first wall surface portion in contact with a stator core of the rotating electric machine and a second wall surface portion in contact with an oil passage through which the oil passes, It is possible to circulate cooling water,
In the operating state of the water pump, in at least a part of the first operation region in which the torque of the rotating electric machine is equal to or more than a predetermined first threshold, the electric oil pump is operated, and the torque of the rotating electric machine is reduced. In at least a part of the second operation region where the rotation speed of the rotating electric machine is smaller than the first threshold value and larger than a predetermined second threshold value, the discharge amount of the electric oil pump is set to be smaller than in the operation state. Cooling control device to reduce.