JP2021083210A - Rotary electric machine and drive unit - Google Patents

Abstract

To increase a resonance frequency of a driving unit in which a rotary electric machine is used.SOLUTION: A rotary electric machine comprises: a stator and a rotor; and a first case housing the stator and the rotor. The first case includes: a housing with one end side in an axial direction being open; and a cover fixed to the housing so as to fix the stator and cover the one end side of the housing . The cover includes an annular rib projecting from an inner face toward the other end side of the housing, and the annular rib has a plurality of boss parts to which a bolt for fastening the stator threadedly engage at intervals in a peripheral direction.SELECTED DRAWING: Figure 3

Description

The present disclosure relates to a rotary electric machine and a drive unit.

Conventionally, as a rotary electric machine of this type, one including a stator and a rotor and a case for accommodating the stator and the rotor has been proposed (see, for example, Patent Document 1). In this rotary electric machine, the case has a housing having one end side opened in the axial direction, and a cover fixed to the housing so as to cover one end side of the housing while the stator is fixed. A plurality of boss portions into which bolts for fastening the stator are screwed are formed on the cover at intervals in the circumferential direction.

Japanese Unexamined Patent Publication No. 2009-101730

In a drive unit in which such a rotary electric machine is used, if the rigidity around the boss portion of the cover, and by extension, the rigidity of the integrated stator and case is low, the resonance frequency of the drive unit becomes low, and the rotation speed of the output shaft of the drive unit becomes low. Vibration and noise may increase in a low frequency region (for example, when mounted on a vehicle, a low vehicle speed region).

An object of the present invention is to increase the resonance frequency of a drive unit in which a rotary electric machine is used.

The rotary electric machine of the present disclosure has adopted the following means in order to achieve the above-mentioned main object.

The rotary electric machine of the present disclosure is
A rotary electric machine including a stator and a rotor and a first case for accommodating the stator and the rotor.
The first case has a housing having one end opened in the axial direction, and a cover to which the stator is fixed and fixed to the housing so as to cover the one end side of the housing.
The cover has an annular rib that projects from the inner surface toward the other end side of the housing.
A plurality of boss portions into which bolts for fastening the stator are screwed are formed on the annular rib at intervals in the circumferential direction.
The gist is that.

In the rotary electric machine of the present disclosure, the first case has a housing having one end side opened in the axial direction and a cover fixed to the housing so as to cover one end side of the housing while the stator is fixed. The annular rib has an annular rib protruding from the inner surface toward the other end side of the housing, and the annular rib is formed with a plurality of boss portions into which bolts for fastening the stator are screwed at intervals in the circumferential direction. ing. As a result, the rigidity around the boss portion of the cover, and by extension, the rigidity of the integrated stator and the first case can be increased. Therefore, the resonance frequency of the drive unit in which the rotary electric machine is used can be increased. As a result, it is possible to suppress an increase in vibration and noise in a region where the rotation speed of the output shaft of the drive unit is low (for example, in a low vehicle speed region when mounted on a vehicle).

It is a schematic block diagram of the hybrid vehicle 10 equipped with the rotary electric machine of this disclosure. It is sectional drawing around the motor MG and the clutch C1 of a hybrid vehicle 10. It is a perspective view of the front cover 80 of a case 70.

Next, a mode for carrying out the invention of the present disclosure will be described with reference to the drawings.

FIG. 1 is a schematic configuration diagram of a hybrid vehicle 10 equipped with a drive unit having a rotary electric machine according to the present disclosure. As shown in the figure, the hybrid vehicle 10 of the present disclosure includes an engine 11, a motor (rotary electric machine) MG, a clutch C1, and a power transmission device 15. Here, the motor MG and the power transmission device 15 correspond to the "drive unit" of the embodiment.

The engine 11 is configured as an internal combustion engine that outputs power using fuel such as gasoline or light oil. The crankshaft 12 of the engine 11 is connected to the first transmission shaft 14a via a damper 13. The damper 13 has a plurality of coil springs (elastic bodies) that damp the torsional vibration.

The motor MG is configured as a well-known synchronous motor generator, and is rotationally driven by an inverter (not shown). The clutch C1 is configured as a hydraulically driven friction clutch, and connects and disconnects the first transmission shaft 14a and the motor MG.

The power transmission device 15 includes a torque converter 16, an automatic transmission (transmission mechanism) 17, an oil pump 18, and a hydraulic control device 19. The torque converter 16 is configured as a general fluid transmission device, and is a pump impeller attached to a second transmission shaft 14b connected to a motor MG and a turbine runner connected to an input shaft 17i of an automatic transmission 17. A stator that rectifies the flow of hydraulic oil from the turbine runner to the pump impeller, a one-way clutch that limits the direction of rotation of the stator in one direction, and a hydraulic drive that connects and disconnects the pump impeller and turbine runner. Equipped with a lockup clutch. The torque converter 16 amplifies and transmits the power of the second transmission shaft 14b to the input shaft 17i of the automatic transmission 17, or transmits the torque without amplifying the torque.

The automatic transmission 17 is configured as, for example, a 4-speed to 10-speed transmission, and includes an input shaft 17i, an output shaft 17o connected to a drive wheel DW via a differential gear DF, and a plurality of planetary gears. It is equipped with a plurality of hydraulically driven friction engaging elements (clutch, brake). The automatic transmission 17 shifts the power transmitted to the input shaft 17i in a plurality of stages and outputs the power from the output shaft 17o. A continuously variable transmission may be used instead of the automatic transmission 17.

The oil pump 18 is attached to the pump impeller of the torque converter 16 and is driven by the power of the second transmission shaft 14b. The hydraulic control device 19 has a valve body and a plurality of valves, and regulates the oil pressure from the oil pump 18 to supply it to the lockup clutch of the torque converter 16 and the clutch and brake of the automatic transmission 17.

FIG. 2 is a cross-sectional view of the hybrid vehicle 10 around the motor MG and the clutch C1. As shown in FIG. 2, the motor MG includes a stator 20, a rotor 30 arranged radially inside the stator 20, and a case 70 that houses the stator 20 and the rotor 30 and has a housing 71 and a front cover 80. Be prepared.

The stator 20 includes a stator core 21 and a three-phase coil 22 wound around the stator core 21. The stator core 21 is integrally formed by, for example, laminating a plurality of electromagnetic steel sheets formed in an annular shape by press working and connecting them in the stacking direction, and is fixed to the front cover 80 of the case 70 by bolts 25.

The rotor 30 includes a rotor core 31 and a holding member 40 that holds the rotor core 31. The rotor core 31 is formed by, for example, laminating a plurality of electromagnetic steel sheets formed in an annular shape by press working, and has a plurality of through holes formed so as to penetrate in the axial direction at intervals in the circumferential direction. Permanent magnets 31a are embedded in each. End plates 32 and 33 are arranged on both ends of the rotor core 31 in the axial direction.

The holding member 40 includes an outer member 41 and an inner member 45 welded to the outer member 41. The outer member 41 is formed by, for example, forging and cutting iron, and has a tubular tubular portion 42 and a flange extending radially outward from one end portion (left end portion in FIG. 2) of the tubular portion 42. A portion 43 and an annular wall portion 44 extending radially inward from the other end side (right side in FIG. 2) of the tubular portion 42 with respect to the center in the axial direction are provided. The rotor core 31 is attached to the tubular portion 42 together with the end plates 32 and 33 by shrink fitting as follows.

First, the rotor core 31 formed to have an inner diameter slightly smaller than the outer diameter of the tubular portion 42 of the holding member 40 is heated, and the rotor core 31 is heated so that the inner diameter of the rotor core 31 is larger than the outer diameter of the tubular portion 42. Inflate. Subsequently, the end plate 32, the rotor core 31, and the end plate 33 are arranged in this order from the flange portion 43 side so as to surround the tubular portion 42 and abut each other, and the end plate 32 abuts on the flange portion 43. Then, when the rotor core 31 is cooled, the rotor core 31 and the tubular portion 42 are fixed by the contraction of the rotor core 31. Then, the end plate 33 is fixed to the tubular portion 42 by caulking or the like of the end plate 33.

The inner member 45 is formed by, for example, forging and cutting iron, and has a tubular shape extending from the inner circumference of the annular wall portion 46 and the annular wall portion 46 to one side in the axial direction (left side in FIG. 2). The tubular portion 47, the tubular portion 48 extending from the radial outside to the other side (right side in FIG. 2) in the axial direction from the tubular portion 47 of the annular wall portion 46, and the annular wall portion 46. It is provided with a protruding portion 49 having a triangular cross section and extending from the outer side in the radial direction to one side in the axial direction with respect to the tubular portion 48.

The outer circumference of the annular wall portion 46 is fixed to the inner circumference of the annular wall portion 44 of the outer member 41 by welding. The inner circumference of the tubular portion 47 is spline-fitted to the outer circumference of the second transmission shaft 14b. A bearing 90 is arranged between the outer circumference of the tubular portion 48 and the inner circumference of the tubular portion 75 of the housing 71. Therefore, the tubular portion 48 is rotatably supported by the housing 71 via the bearing 90.

A connecting member 51 is fixed by bolts 50 on the side of the flange portion 43 of the holding member 40 opposite to the rotor core 31. The connecting member 51 is formed of, for example, iron, has a fixing portion (bolt hole) with the flange portion 43 on the outer peripheral portion, and has a plate-shaped annular wall portion 52 and one side in the axial direction from the inner circumference of the annular wall portion 52. It has a tubular tubular portion 53 extending to the flange. A bearing 91 is arranged between the outer circumference of the tubular portion 53 and the inner circumference of the tubular portion 85 of the front cover 80, and between the inner circumference of the tubular portion 53 and the first transmission shaft 14a. , Bearing 92 is arranged. As a result, the connecting member 51 and the holding member 40 connected to the connecting member 51 are rotatably supported by the front cover 80 via the bearing 91, and the first transmission shaft 14a is relative to the connecting member 51 via the bearing 92. It is rotatably supported.

As a result, a space is formed inside the tubular portion 42 of the holding member 40 in the radial direction so that both sides in the axial direction are partitioned by the annular wall portions 44 and 46 of the holding member 40 and the annular wall portions 52 of the connecting member 51. Will be done.

The clutch C1 includes a clutch hub 61 connected to a first transmission shaft 14a, a holding member 40 connected to a second transmission shaft 14b and also functioning as a clutch drum, a plurality of friction plates 63, and a friction plate 63. A plurality of alternately arranged separator plates 64, a backing plate 65, a snap ring 66, a piston 67 that presses and frictionally engages the separator plate 64 and the friction plate 63, a plurality of return springs SP, and cancellation. A plate (cancellation oil chamber drawing member) 68 is provided.

The clutch hub 61 includes a tubular tubular portion 61a and an annular wall portion 61b extending radially inward from one end of the tubular portion 61a. Splines 61s are formed on the outer peripheral surface of the tubular portion 61a. The inner circumference of the annular wall portion 61b is connected to the first transmission shaft 14a by welding.

Splines 42s are formed on the inner peripheral surface of the tubular portion 42 of the holding member 40 that also functions as a clutch drum on the flange portion 43 side of the annular wall portion 44. The spline 42s is formed with an annular recess 42a that is recessed outward in the radial direction. The annular recess 42a overlaps the end surface of the flange portion 43 on the rotor core 31 side (the end surface on the right side in FIG. 2) in the axial direction of the rotor 30 when viewed from the radial direction of the rotor 30.

Each of the plurality of friction plates 63 is an annular member to which a friction material is attached to both sides, and the outer peripheral portion thereof is fitted to the spline 42s of the tubular portion 42 of the holding member 40 (clutch drum). As a result, the plurality of friction plates 63 rotate integrally with the tubular portion 42 and are supported by the tubular portion 42 so as to be movable in the axial direction.

Each of the plurality of separator plates 64 is an annular member having smooth surfaces formed on both sides, and the inner peripheral portion thereof is fitted to the spline 61s of the clutch hub 61. As a result, the plurality of separator plates 64 rotate integrally with the clutch hub 61 and are supported by the clutch hub 61 so as to be movable in the axial direction.

The backing plate 65 is an annular member, and its outer peripheral portion is fitted to the spline 42s of the tubular portion 42 so as to be in contact with the friction plate 63 farthest from the piston 67 among the plurality of friction plates 63. The snap ring 66 is attached (fitted) to the annular recess 42a of the tubular portion 42. The snap ring 66 regulates the axial movement of the backing plate 65 and the like (movement on the side away from the piston 67).

The piston 67 has an annular pressure receiving portion 67a, a tubular tubular portion 67b extending from the outer circumference of the pressure receiving portion 67a toward the clutch hub 61 in the axial direction, and a pressing force extending radially outward from the tubular portion 67b. A unit 67c is provided.

The inner peripheral surface of the pressure receiving portion 67a is movably supported in the axial direction by the outer peripheral surface of the tubular portion 47 of the holding member 40 via the sealing member. The outer peripheral surface of the pressure receiving portion 67a is movably supported in the axial direction by the inner peripheral surface of the protruding portion 49 of the holding member 40 via the sealing member. The engaging oil chamber 69a of the clutch C1 is defined by the annular wall portion 46 and the tubular portions 47 and 49 of the holding member 40 and the pressure receiving portion 67a of the piston 67. The engaging oil chamber 69a is connected to the hydraulic control device 19 via an oil passage (not shown), and the engaging oil chamber 69a is connected to the engaging oil pressure (hydraulic oil) regulated by the hydraulic control device 19. Is supplied. When the engaging oil chamber 69a is supplied with the engaging oil, the piston 67 moves toward the cancel plate 68 by the action of the engaging oil, and the pressing portion 67c presses the separator plate 64 and the friction plate 63. As a result, the clutch C1 is engaged.

On the outer peripheral surface of the pressing portion 67c, a plurality of recesses (grooves) loosely fitted to the splines 42s of the tubular portion 42 of the holding member 40 are formed at intervals in the circumferential direction. As a result, the piston 67 can be prevented from rotating with respect to the tubular portion 42, and both can be rotated integrally.

The cancel plate 68 is an annular member arranged on the side opposite to the annular wall portion 46 of the holding member 40 with respect to the piston 67, and the inner peripheral portion thereof is a tubular portion 47 of the holding member 40 using a snap ring. Is fixed to. The outer peripheral surface of the cancel plate 68 supports the inner peripheral surface of the tip end portion of the tubular portion 67b of the piston 67 so as to be movable in the axial direction via a sealing member. The pressure receiving portion 67a and the tubular portion 67b of the piston 67, the cancel plate 68, and the tubular portion 47 of the holding member 40 define a centrifugal oil pressure canceling chamber 69b for canceling the centrifugal oil pressure generated in the engaging oil chamber. Ru. The centrifugal hydraulic pressure canceling chamber 69b is connected to the hydraulic control device 19 via an oil passage (not shown), and the centrifugal hydraulic pressure canceling chamber 69b is filled with hydraulic oil for lubrication / cooling drained from the hydraulic control device 19. A part of the holding member 40 is supplied through the oil passage by the centrifugal force generated by the rotation of the holding member 40 and the like.

The plurality of return springs 69 are arranged at intervals in the circumferential direction between the pressure receiving portion 67a of the piston 67 and the cancel plate 68 in the axial direction, and are attached to the side of the piston 67 away from the friction plate 63 and the separator plate 64. Momentum. As the return spring 69, for example, a coil spring is used.

The case 70 includes a housing 71 in which the engine 11 side (left side in FIG. 2) opens in the axial direction, and a front cover 80 fixed to the housing 71 so as to cover one end side (opening side) of the housing 71.

The housing 71 is formed by casting an aluminum alloy or the like, and has an annular wall portion 72, a tubular portion 73 extending from the outer circumference of the annular wall portion 72 toward the engine 11 in the axial direction, and the tip of the tubular portion 73. An extension portion 74 extending in this order from the outer circumference on the side in the radial direction, the engine 11 side in the axial direction, and the outer circumference in the radial direction, and a tubular portion in the axial direction from slightly outside in the radial direction from the inner circumference of the annular wall portion 72. It has a tubular portion 75 extending to the same side as 73, and a tubular portion 76 extending from the outer circumference of the annular wall portion 72 to a side (power transmission device 15 side) separated from the engine 11 in the axial direction.

A female screw hole 73h having an opening at the tip surface is formed at the tip of the tubular portion 73 at intervals in the circumferential direction. A plurality of bolt holes (through holes) 74h that penetrate in the axial direction at intervals in the circumferential direction are formed in the extending portion 74. The extension portion 74 has a plurality of bolts (not shown) inserted into the corresponding bolt holes 74h and the corresponding female screw holes (not shown) formed in the engine block 110 (see FIG. 1) of the engine 10. By screwing, it is fixed to the engine block 110.

As described above, the tubular portion 75 rotatably supports the tubular portion 48 of the holding member 40 via the bearing 90. The tubular portion 76 is formed with a plurality of bolt holes (through holes) 76h that penetrate in the axial direction at intervals in the circumferential direction. The tubular portion 76 has a plurality of bolts (not shown) inserted into the corresponding bolt holes 76h and corresponding female screw holes (not shown) formed in the transmission case 150 (see FIG. 1) of the power transmission device 15. ), It is fixed to the transmission case 150.

FIG. 3 is a perspective view of the front cover 80 of the case 70. The front cover 80 is formed by casting a material having a coefficient of thermal expansion larger than that of the material forming the stator core 21 of the stator 20, for example, an aluminum alloy. As shown in FIGS. 2 and 3, the front cover 80 includes a plate-shaped annular wall portion 81, an extension portion 82 extending radially outward from the outer circumference of the annular wall portion 81, and an annular wall portion 81. An annular rib 83 extending from the outer circumference to the housing 71 side (right side in FIG. 2) in the axial direction, and a plurality of (for example, eight) boss portions 84 formed on the annular rib 83 at intervals in the circumferential direction. It is provided with a tubular portion 85 extending from slightly outside in the radial direction to the housing 71 side in the axial direction with respect to the inner circumference of the annular wall portion 81.

A plurality of bolt holes (through holes) 82h are formed in the extending portion 82 at intervals in the circumferential direction. The extension portion 82 is formed into the tubular portion 73 of the housing 71 by inserting a plurality of bolts 94 into the corresponding bolt holes 82h and screwing them into the corresponding female screw holes 73h of the tubular portion 73 of the housing 71. It is fixed.

Extending portions 83a extending in the axial direction from the outer periphery of the tip end portion of the annular rib 83 are formed on both sides of each boss portion 84 of the annular rib 83 in the circumferential direction. The inner diameter of the annular rib 83 is designed to be smaller than the outer diameter of the stator core 21, and the inner diameter of the extending portion 83a is designed to be slightly larger than the outer diameter of the stator core 21.

Further, between the two adjacent boss portions 84 of the annular rib 83, the V is opened on the tip side and the length in the axial direction is shorter than that of the annular rib 83 (for example, about half of the annular rib 83). A letter-shaped notch 83b is formed. Specifically, the plurality of notches 83b are formed at equal intervals in the circumferential direction of the annular rib 83. The shape of the notch 83b is not limited to a V shape, and is appropriately designed.

Female screw holes 84h are formed in each of the plurality of boss portions 84. One end side (left side in FIG. 2) of the stator core 21 is positioned by the inner circumferences of the plurality of extending portions 83a, and the plurality of bolts 25 are respectively inserted into the corresponding bolt holes 21h of the stator core 21 and a plurality of bolts 25 are inserted. By screwing into the corresponding female screw holes 84h of the boss portion 84, the front cover 80 is fixed to the plurality of boss portions 84.

The friction plate 63 and the separator plate 64 of the clutch C1 are provided by hydraulic oil supplied between the clutch hub 61 and the cancel plate 68 or through an oil hole formed in the tubular portion 61a of the clutch hub 61. , Lubrication and cooling are performed. Then, at least a part of the hydraulic oil is between the oil holes formed in the tubular portion 42 of the holding member 40 and the rotor core 31 of the rotor 30 and the tubular portion 42 and the flange portion 43 of the holding member 40. The rotor 30 is cooled by circulating the above. Further, at least a part of the hydraulic oil is supplied to the coil end 22 of the stator 20 and the like to cool the stator 30.

In the present embodiment, the front cover 80 of the case 70 has an annular rib 83 and a plurality of boss portions 84 formed on the annular rib 83 at intervals in the circumferential direction. Then, in the stator core 21, the plurality of bosses of the front cover 80 are formed by inserting the plurality of bolts 25 into the corresponding bolt holes 21h of the stator core 21 and screwing them into the corresponding female screw holes 84h of the plurality of boss portions 84. It is fixed to the portion 84. By providing the annular rib 83 in this way, the rigidity around the plurality of boss portions 84 of the front cover 80, and by extension, the rigidity of the integrated stator 20 and the case 70 (housing 71 and case 80) can be increased. .. Therefore, the resonance frequency of the drive unit having the motor MG and the power transmission device 15 can be increased. As a result, it is possible to suppress an increase in vibration and noise in a region where the rotation speed of the output shaft 17o is low (low vehicle speed region).

Further, in the embodiment, the front cover 80 of the case 70 is formed of a material having a coefficient of thermal expansion larger than that of the material forming the stator core 21 of the stator 20, and two adjacent annular ribs 83 of the front cover 80 are adjacent to each other. A notch 83b that opens on the tip side is formed between the boss portions 84, respectively. As a result, the rigidity around the boss portion 84 of the front cover 80 is lower than that in which the notch 83b is not formed. Therefore, when the front cover 80 is thermally expanded due to heat generated by the motor MG or the like, the front cover 80 is deformed. The bolt 25 makes it easier to hold. Moreover, since the plurality of notches 83b are formed in a V shape, the thermal expansion of the front cover 80 can be more easily absorbed by the plurality of notches 83b while ensuring the rigidity of the front cover 80 to some extent.

As a result, it is possible to prevent the plurality of bolts 25 from loosening with respect to the corresponding female screw holes 84h of the plurality of boss portions 84. Further, the hydraulic oil in the case 70 (the hydraulic oil supplied to the clutch C1, the motor MG, etc.) can be circulated through the notch 83b at the lower part of the front cover 80. By forming the plurality of notches 83b at equal intervals in the circumferential direction of the annular rib 83, vibration and noise of the drive unit can be reduced, and loosening of the plurality of bolts 25 with respect to the plurality of female screw holes 84h can be suppressed. It is possible to properly achieve both.

Further, in the embodiment, a plurality of extending portions 83a extending in the axial direction from the outer periphery of the tip end portion of the annular rib 83 of the front cover 80 are formed. By using the plurality of extending portions 83a for positioning the stator core 21, the stator 20 can be easily fastened to the stator core 21.

In the embodiment, it is assumed that a notch 83b is formed between two adjacent boss portions 84 of the annular rib 83 of the front cover 80, respectively. That is, the number of boss portions 84 and the number of notches 83b are assumed to be the same. However, the number of notches 83b may be smaller than the number of boss portions 84. Even in this case, it is preferable that the plurality of notches 83b are formed at equal intervals in the circumferential direction of the annular rib 83. For example, when there are 6 boss portions 84, 3 notches 83b are formed every 120 degrees, and when there are 8 boss portions 84, 4 notches 83b are formed every 90 degrees. It may be a thing. Further, the notch 83b may not be formed in the annular rib 83.

In the embodiment, the front cover 80 has a plurality of extension portions 83a, but may not have such a plurality of extension portions 83a.

As described above, the rotary electric machine of the present disclosure is a rotary electric machine (MG) including a stator (20) and a rotor (30), and a first case (70) for accommodating the stator (20) and the rotor. In the first case (70), the housing (71) having one end side opened in the axial direction and the stator (20) are fixed and the one end side of the housing (71) is covered. The cover (80) has a cover (80) fixed to the housing (71), and the cover (80) has an annular rib (83) protruding from the inner surface toward the other end side of the housing (71). The gist is that the annular rib (83) is formed with a plurality of boss portions (84) into which bolts (25) for fastening the stator (20) are screwed at intervals in the circumferential direction. To do.

In the rotary electric machine of the present disclosure, the first case has a housing having one end side opened in the axial direction and a cover fixed to the housing so as to cover one end side of the housing while the stator is fixed. The annular rib has an annular rib protruding from the inner surface toward the other end side of the housing, and the annular rib is formed with a plurality of boss portions into which bolts for fastening the stator are screwed at intervals in the circumferential direction. ing. As a result, the rigidity around the boss portion of the cover, and by extension, the rigidity of the integrated stator and the first case can be increased. Therefore, the resonance frequency of the drive unit in which the rotary electric machine is used can be increased. As a result, it is possible to suppress an increase in vibration and noise in a region where the rotation speed of the output shaft of the drive unit is low (for example, in a low vehicle speed region when mounted on a vehicle).

In the rotary electric machine of the present disclosure, a plurality of notches (83b) are formed at equal intervals in the circumferential direction between the two adjacent boss portions (84) of the annular rib (83). It may be a thing. In this way, it is possible to prevent the bolt for fastening the stator and the cover from loosening with respect to the boss portion. Further, the hydraulic oil (cooling medium) supplied to the rotary electric machine can be circulated through the notch in the lower part of the first case.

In this case, the plurality of notches may be formed in a V shape. In this way, the thermal expansion of the cover can be more easily absorbed by the plurality of notches while ensuring the rigidity of the cover to some extent.

Further, in this case, the cover (80) may be made of a material having a coefficient of thermal expansion larger than that of the material forming the stator (20). Since the cover expands more easily than the stator, it is more significant to provide a plurality of notches in the annular rib to prevent the bolts for fastening the stator and the cover from loosening with respect to the boss portion. ..

In the rotary electric machine of the present disclosure, a positioning portion (83a) of the stator (20) may be formed at the tip end portion of the annular rib (83). In this way, the stator and the cover can be fastened more easily.

The drive unit of the present disclosure includes a power transmission device (15) that transmits the power of the transmission shaft (14b) connected to the rotary electric machine (MG) to the output shaft (17o), and the first case (70) The gist is that the power transmission device (15) is fixed to the second case (150). Since the drive unit of the present disclosure includes the rotary electric machine of the present disclosure in any of the above-described aspects, it is possible to obtain the same effect as that of the rotary electric machine of the present disclosure.

Although the embodiments for carrying out the present disclosure have been described above, the present disclosure is not limited to these embodiments, and can be implemented in various forms without departing from the gist of the present disclosure. Of course.

The present disclosure can be used in the manufacturing industry of rotary electric machines and drive units having the same.

10 Hybrid vehicle, 11 engine, 12 crankshaft, 13 damper, 14a 1st transmission shaft, 14b 2nd transmission shaft, 15 power transmission device, 16 torque converter, 17 automatic transmission, 17i input shaft, 17o output shaft, 18 oil Pump, 19 hydraulic control device, 20 stator, 21 stator core, 21h bolt hole, 22 three-phase coil, 25, 50, 94 volt, 30 rotor, 31 rotor core, 31a permanent magnet, 32, 33 end plate, 40 holding member, 41 Outer member, 42,47,48,53,61a, 73,75,85 Cylindrical part, 42a annular recess, 42s, 61s spline, 43 flange part, 44,46,52,61b, 72,81 annular wall part, 45 Inner member, 49 Protruding part, 51 Connecting member, 61 Clutch hub, 63 Friction plate, 64 Separator plate, 65 Backing plate, 66 Snap ring, 67 Piston, 67a Pressure receiving part, 67c Pressing part, 68 Cancel plate, 69 Return spring , 69a Engagement oil chamber, 69b Centrifugal hydraulic cancellation chamber, 70 case, 71 housing, 73h, 84h female screw hole, 74,82,83a extension part, 74h, 82h bolt hole, 80 front cover, 83 annular rib, 83b notch , 84 Boss, 90, 91, 92 bearings, 110 engine block, 150 transmission case, C1 clutch.

Claims (6)

A rotary electric machine including a stator and a rotor and a first case for accommodating the stator and the rotor.
The first case has a housing having one end opened in the axial direction, and a cover to which the stator is fixed and fixed to the housing so as to cover the one end side of the housing.
The cover has an annular rib that projects from the inner surface toward the other end side of the housing.
A plurality of boss portions into which bolts for fastening the stator are screwed are formed on the annular rib at intervals in the circumferential direction.
Rotating electric machine. The rotary electric machine according to claim 1.
A plurality of notches are formed at equal intervals in the circumferential direction between the two adjacent boss portions of the annular rib.
Rotating electric machine. The rotary electric machine according to claim 2.
The plurality of notches are formed in a V shape.
Rotating electric machine. The rotary electric machine according to claim 2 or 3.
The cover is made of a material having a higher coefficient of thermal expansion than the material forming the stator.
Rotating electric machine. The rotary electric machine according to any one of claims 1 to 4.
A positioning portion of the stator is formed at the tip of the annular rib.
Rotating electric machine. A drive unit including the rotary electric machine according to any one of claims 1 to 5.
A power transmission device for transmitting the power of the transmission shaft connected to the rotary electric machine to the output shaft is provided.
The first case is fixed to the second case of the power transmission device.
Drive unit.

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