Rotating electric machine and vehicle-mounted configuration of rotating electric machine

Abstract

A rotary electric machine (100F) has a cylindrical outer housing (1o) and a cylindrical inner housing (1i) that forms a cooling liquid flow path between the outer housing (1o). The inner housing (1i) is fixed to the outer housing at one end in the axial direction by press-fitting or shrink-fitting and is fastened to the outer housing (1o) at the other end by a plurality of bolts (5). At the fixed portion of the outer housing (1o) and the inner housing (1i) by press-fitting or shrink-fitting, a non-contact portion (1p) that makes the inner peripheral surface of the outer housing (1o) and the outer peripheral surface of the inner housing (1i) not contact each other is formed in the circumferential direction in a number of one or more.

Description

TECHNICAL FIELD

[0001] The present application relates to a rotating electric machine and an installation configuration of the rotating electric machine on a vehicle. BACKGROUND

[0002] Patent Document 1 below discloses a rotating electric machine. With regard to the rotating electric machine, a stator core of a cylindrical shape is installed to an inner peripheral surface of a [tube-shaped] housing by shrink fitting, and a rotor is provided inside the stator core in a rotatable manner. The rotating electric machine generates heat, and in order to cool the heat, a cooling liquid flow path for circulating a cooling liquid is formed inside the housing. In order to form the cooling liquid flow path, the housing is composed of an outer housing of a cylindrical shape, and an inner housing of a cylindrical shape which is inserted inside the outer housing.

[0003] In order to form the cooling liquid flow path without increasing the size of the rotating electric machine, the housing of this double wall configuration is adopted. Specifically, the entire inner housing in which a helical groove is formed on an outer peripheral surface is press-fit or shrink-fit to the inside of the outer housing.

[0004] Patent Document 1: Japanese Patent No. 6314158 SUMMARY

[0005] With regard to the rotating electric machine, vibration of the inner housing is caused by rotation of the rotor. The vibration is transmitted from the inner housing to the outer housing, and radiation sound is generated from the housing to the outside. Sometimes the double cylinder configuration for forming the above-described cooling liquid flow path promotes the radiation sound.

[0006] Therefore, an object of the present application is to provide a rotating electric machine having a double cylinder configuration which is capable of suppressing radiation of noise. In addition, another object of the present application is to provide an installation configuration of the rotating electric machine on a vehicle which is capable of effectively suppressing radiation of noise.

[0007] A first feature of the present application provides a rotating electric machine having: an outer housing of a cylindrical shape; and an inner housing of a cylindrical shape which forms a cooling liquid flow path with the outer housing. The inner housing is fixed to the outer housing by press-fit or shrink-fit at one end in the axial direction, and is fastened to the outer housing by a plurality of bolts at the other end. At the fixed portion by press-fit or shrink-fit, a non-contact portion in which the inner peripheral surface of the outer housing and the outer peripheral surface of the inner housing do not contact is formed in the circumferential direction in a number of one or more.

[0008] The second feature of the present application provides the vehicle-mounted configuration of the rotating electric machine of the above-described first feature. Regarding the vehicle-mounted configuration, the fixed portion is divided into an upper quarter-circumferential range, a lower quarter-circumferential range, a front quarter-circumferential range, and a rear quarter-circumferential range in the circumferential direction as viewed in the axial direction. Here, the total length of the non-contact portions in the front quarter-circumferential range and the rear quarter-circumferential range is greater than the total length of the non-contact portions in the upper quarter-circumferential range and the lower quarter-circumferential range.

[0009] The third feature of the present application provides the vehicle-mounted configuration of the rotating electric machine of the above-described first feature. Regarding the vehicle-mounted configuration, the fixed portion is divided into a passenger compartment side range close to the passenger compartment and an opposite side range on the opposite side of the passenger compartment as viewed in the axial direction. Here, the total length of the non-contact portions in the passenger compartment side range is greater than the total length of the non-contact portions in the opposite side range.

[0010] Effects of the Invention

[0011] According to the above-described first feature, it is possible to provide a rotating electric machine capable of suppressing radiation of sound. In addition, according to the above-described second feature, it is possible to more effectively suppress the radiation sound of the rotating electric machine mounted on a vehicle. Furthermore, according to the above-described third feature, it is possible to more effectively suppress the radiation of the radiation sound of the rotating electric machine mounted on a vehicle toward the passenger compartment. BRIEF DESCRIPTION OF DRAWINGS

[0012] Figure 1 is an exploded perspective view of a rotating electric machine (front MG) according to an embodiment.

[0013] Figure 2 is a cross-sectional view of the above-described front MG including a center O of a rotating shaft.

[0014] Figure 3 is a side view of the above-described front MG as viewed in the direction of the above-described rotating shaft.

[0015] Figure 4 is a cross-sectional view of line IV-IV in Figure 2 .

[0016] Figure 5A is a schematic perspective view showing vibration of an inner housing (opposite phase vibration).

[0017] Figure 5B is a schematic perspective view showing vibration of an inner housing (same phase vibration).

[0018] Figure 6 is a perspective view of another rotating electric machine (rear MG) according to an embodiment.

[0019] Figure 7 is a side view of the above-described rear MG as viewed in the direction of the rotating shaft.

[0020] Figure 8A is an explanatory diagram schematically showing a circular ring 0th order vibration mode of the inner case.

[0021] Figure 8B is an explanatory diagram schematically showing a circular ring 1st order vibration mode of the inner case.

[0022] Figure 8C is an explanatory diagram schematically showing a circular ring 2nd order vibration mode of the inner case.

[0023] Figure 8D is an explanatory diagram schematically showing a circular ring 3rd order vibration mode of the inner case.

[0024] Figure 8E is an explanatory diagram schematically showing a circular ring 4th order vibration mode of the inner case.

[0025] Figure 8F is an explanatory diagram schematically showing a circular ring 5th order vibration mode of the inner case.

[0026] Figure 9A is a side view showing the vehicle-mounted configuration of the above front MG (first example).

[0027] Figure 9B is a side view showing the vehicle-mounted configuration of the above rear MG (first example).

[0028] Figure 10 is a side view showing the vehicle-mounted configuration of the above front MG and the above rear MG (second A example).

[0029] Figure 11A is a side view showing the vehicle-mounted configuration of the front MG of the above second A example.

[0030] Figure 11B is a side view showing the vehicle-mounted configuration of the rear MG of the above second A example.

[0031] Figure 12 is a side view showing the vehicle-mounted configuration of the above front MG and the above rear MG (second B example).

[0032] Figure 13A is a side view showing the vehicle-mounted configuration of the front MG of the above second B example.

[0033] Figure 13B is a side view showing the vehicle-mounted configuration of the rear MG of the above second B example.

[0034] Figure 14 is a side view showing the vehicle-mounted configuration of the above front MG and the above rear MG (second C example).

[0035] Figure 15A is a side view showing the vehicle-mounted configuration of the front MG of the above second C example.

[0036] Figure 15B is a side view showing the vehicle-mounted configuration of the rear MG of the above-described second C example. DETAILED DESCRIPTION

[0037] Hereinafter, a rotating electric machine according to an embodiment will be described with reference to the drawings.

[0038] The rotating electric machine of the present embodiment is a motor-generator (MG) mounted on a vehicle, which can function as an electric motor and also as a generator. In the present embodiment, as a rotating electric machine, a front MG 100F is mounted on a front portion of a vehicle V to drive a front wheel FW, and a rear MG 100R is mounted on a rear portion of the vehicle V to drive a rear wheel RW (see FIG. 1). The front MG 100F and the rear MG 100R can also generate electric power by regenerative operation when the vehicle V is decelerating. Figure 10 ) The front MG 100F and the rear MG 100R can also generate electric power by regenerative operation when the vehicle V is decelerating.

[0039] First, the front MG 100F will be described. Figure 1 is an exploded oblique view of a housing 1 of the front MG 100F. The housing 1 has a double pipe configuration composed of an outer housing 1o and an inner housing 1i. The housing 1 will be described in detail. Further, the front MG 100F of the present embodiment also integrally has a front gear unit 101F. The front gear unit 101F has a reduction gear set and a differential gear inside. A rotary shaft of a rotor 3 of the front MG 100F, which will be described later, is mechanically connected to a drive shaft DS of the front wheel FW via the reduction gear set and the differential gear. Further, the drive shaft DS in the figure is shown schematically with the omission of a constant velocity joint or the like. A part of the housing of the front gear unit 101F is integrated with the above-described outer housing 1o.

[0040] Figure 2 is a cross-sectional view of the front MG 100F including a center O of a rotary shaft. The front MG 100F has a stator 2 and a rotor 3 inside the housing 1. The stator 2 is embedded inside the inner housing 1i, and has a stator core 2s and a coil 2c, like a general electric machine. The stator core 2s is composed of a plurality of metal laminated plates (electromagnetic steel plates) laminated in the direction of the rotary shaft (i.e., an axial direction). A plurality of slots 2a are formed at equal intervals on the inner peripheral surface of the stator core 2s. The coil 2c is wound inside the slots 2a. Both ends of the coil 2c in the wound state protrude in the axial direction from both ends of the stator core 2s to form coil ends. Figure 2 The coil ends are shown simply in the middle.

[0041] The rotor 3 is rotatably supported to the housing 1 at both ends thereof via ball bearings 3a. Further, Figure 2The rotor 3 is omitted in part, and the rotating shaft is shown alone in a manner that the stator core 2s described above can be seen.

[0042] The outer housing 1o and the inner housing 1i that constitute the housing 1 are formed of an aluminum alloy. As shown in Figure 1 , the inner housing 1i is formed in a cylindrical shape, and a spiral groove 1g as a flow path of a coolant for cooling the front MG 100F is formed on an outer circumferential surface thereof. A seal groove 1a and 1b for housing seal rings 6a and 6b (see Figure 2 ) for ensuring the liquid tightness of the flow path of the coolant are also formed on the outer circumferential surface of the inner housing 1i. The seal groove 1a is formed on the one end (right end in Figure 2 ) side of the inner housing 1i, and the seal groove 1b is formed on the other end (left end in Figure 2 ) side opposite to the one end side.

[0043] The one end of the inner housing 1i functions as a fixed inner circumferential portion [inner fixed circumferential portion] 1c that is fixed to the outer housing 1o by press-fitting. Only the fixed inner circumferential portion 1c of the inner housing 1i is fixed to a fixed outer circumferential portion [outer fixed circumferential portion] 1n of the outer housing 1o by press-fitting. The press-fitting length (axial length of the fixation area X) is short. In the axial direction, Figure 2 , a fixation area [fixation area] X in which the inner housing 1i and the outer housing 1o are fixed by press-fitting is shown. In addition, the inner housing 1i (fixed inner circumferential portion 1c) and the outer housing 1o (fixed outer circumferential portion 1n) can be fixed to each other by shrink-fitting in the fixation area X.

[0044] In addition, as described above, the stator core 2s is shrink-fitted to the inner housing 1i, Figure 2 , a shrink-fit area [shrink-fit area] Y of the inner housing 1i and the stator core 2s in the axial direction is also shown. The outer diameter of the stator core 2s is set to be slightly larger than the inner diameter of the inner housing 1i. The difference in diameter is called an "interference" (shrink-fitting is also called interference-fit). Furthermore, in a state in which one of the two members is thermally expanded or thermally contracted to generate a thermal deformation that is greater than or equal to the interference, the two members are fitted. If the thermal deformation is restored, the two members are firmly fixed to each other by the interference. In the present embodiment, the stator core 2s is constituted by a plurality of metal laminated plates (and also has the coil 2c wound therearound), and thus the inner housing 1i is thermally expanded to perform shrink-fitting. In general, shrink-fitting can more firmly fix than press-fitting, and the stress after shrink-fitting is greater. In addition, the greater the interference, the greater the stress after shrink-fitting.

[0045] As shown in Figure 1As shown, a flange 1d is formed on the other end of the outer housing 1o so as to project outwardly perpendicularly to the axial direction. A plurality of bolt holes 1e are formed in the flange 1d. As shown in FIG. 2, a plurality of bolt holes 1e are formed in the flange 1d so as to be aligned with the bolt holes 1e of the outer housing 1o. Figure 1 and Figure 3 As shown, a flange 1f is also formed on the other end of the inner housing 1i so as to project outwardly perpendicularly to the axial direction. A bolt insertion hole 1h is formed in the flange 1f. Further, as shown in FIG. 2, a plurality of bolt holes 1e are formed in the flange 1f so as to be aligned with the bolt holes 1e of the outer housing 1o. Figure 3 is a side view of the housing 1 (the outer housing 1o and the inner housing 1i) as viewed in the axial direction from the left side of the vehicle V. However, the stator 2, the rotor 3, and the cover 1t are not shown in FIG. 1. Figure 3 is a side view of the housing 1 (the outer housing 1o and the inner housing 1i) as viewed in the axial direction from the left side of the vehicle V. However, the stator 2, the rotor 3, and the cover 1t are not shown in FIG. 1.

[0046] The other end of the inner housing 1i is fixed to the outer housing 1o via the bolt insertion hole 1h with the bolt 5 (refer to Figure 2 ). That is, the one end of the inner housing 1i is fixed to the outer housing 1o by press-fitting (or shrink-fitting), and the other end of the inner housing 1i is fixed to the outer housing 1o by bolt fastening. Further, positioning holes 1j (refer to Figure 3 ) for positioning pins for positioning both are formed in the flange 1d of the outer housing 1o and the flange 1f of the inner housing 1i. In addition, in the present embodiment, regarding the bolt fastening of the inner housing 1i to the outer housing 1o, as shown in Figure 2 , the cover 1t that closes the other end of the housing 1 is also fastened together.

[0047] As shown in Figure 1 , the outer housing 1o is formed in a cylindrical shape, and a plurality of ribs for ensuring strength and rigidity are formed on the outer peripheral surface thereof. In addition, the outer housing 1o is provided with a supply port 1k that supplies coolant to the coolant flow path formed by the spiral groove 1g of the inner housing 1i and a discharge port 1m that discharges coolant from the coolant flow path. Further, the outer housing 1o is formed in a cylindrical shape, and the front gear unit 101F provided integrally with the outer housing 1o projects to the side from the cylindrical portion of the outer housing 1o.

[0048] One end (the right end in Figure 2 ) of the accommodation chamber of the inner housing 1i of the outer housing 1o is closed by a wall portion. However, a holding portion 1q that holds one end of the rotor 3 by mounting a ball bearing 3a is formed in the center of the wall portion. Further, a hole that leads the rotation axis of the rotor 3 is formed in the center of the holding portion 1q. On the other hand, the other end (the left end in Figure 2 ) of the above-mentioned accommodation chamber is open in order to insert the inner housing 1i in which the stator core 2s is shrink-fitted. The other end of the accommodation chamber is closed by the cover 1t after the inner housing 1i is inserted and the rotor 3 is further assembled inside thereof. A ball bearing 3a is also mounted in the cover 1t, and the other end of the rotor 3 is held.

[0049] According to the above-described double pipe configuration, the cooling liquid flow path can be formed with good space efficiency and easily. In addition, one end of the inner housing 1i is fixed to the outer housing 1o by press-fitting (or shrink fitting), and the other end of the inner housing 1i is fixed to the outer housing 1o by fastening of the bolt 5. That is, the inner housing 1i is fixed to the outer housing 1o at both ends thereof (not fixed in a cantilevered beam shape). Therefore, even if a reaction force of the rotational torque of the front MG 100F acts on the inner housing 1i, torsion or the like does not occur in the inner housing 1i, and the strength and rigidity of the front MG 100F do not decrease, or the acoustic vibration characteristics do not deteriorate.

[0050] In addition, the press-fitting length of the inner housing 1i (fixed inner peripheral portion 1c) and the outer housing 1o (fixed outer peripheral portion 1n) is short, and thus the equipment for press-fitting does not become large-scale. In addition, the press-fitting length can be short and the press-fitting force can be small, and thus the thickness of the fixed inner peripheral portion 1c can be reduced (the inner diameter can be increased), and the gap between the coil end of the coil 2c can be increased. As a result, interference of the inner housing 1i and the coil end (coil 2c) can be prevented at the time of assembly of the rotary electric machine. Furthermore, even in the case where the inner housing 1i and the outer housing 1o are fixed by shrink fitting, only the outer housing 1o (fixed outer peripheral portion 1n) can be locally thermally expanded or contracted, and the equipment for shrink fitting does not become large-scale. In addition, the shrink fitting length is short, and thus the thickness of the fixed inner peripheral portion 1c can be reduced, and interference of the inner housing 1i and the coil end (coil 2c) can be prevented.

[0051] Figure 4 is a cross-sectional view of the fixed portion (fixed range X) of the inner housing 1i and the outer housing 1o by press-fitting (or shrink fitting) as viewed in the axial direction. Furthermore, Figure 4 represents a state in which the inner housing 1i is press-fitted (or shrink fitted) to the outer housing 1o, and the stator 2, the rotor 3, and the cover 1t are not shown. In the present embodiment, in order to suppress radiated sound from the front MG 100F, the non-contact portion 1p in which the inner peripheral surface of the outer housing 1o and the outer peripheral surface of the inner housing 1i do not contact each other is formed at five portions in the circumferential direction in the fixed portion.

[0052] In the present embodiment, the non-contact portion 1p is formed by arranging the inner peripheral surface of the outer housing 1o to the outside with respect to the reference circle, but the non-contact portion 1p can also be formed by arranging the outer peripheral surface of the inner housing 1i to the inside with respect to the reference circle. In addition, the non-contact portion 1p can be formed by arranging the inner peripheral surface of the outer housing 1o to the outside and arranging the outer peripheral surface of the inner housing 1i to the inside. Furthermore, the non-contact portion 1p of the present embodiment is a simple minute gap, but an elastic member such as rubber can be filled in the inside thereof.

[0053] In the interior of the front MG 100F, a magnetic force is generated between the stator 2 and the rotating rotor 3. Therefore, a sound generated in the interior of the front MG 100F, particularly in the interior of the inner housing 1i, is radiated to the outside, and propagates via the outer housing 1o. The above-described non-contact portion 1p cuts off or moderates the propagation of the vibration (sound), and thus can suppress the vibration itself of the inner housing 1i (and the stator 2 which is integrated by the press fitting), and can suppress the propagation and radiation of the vibration sound to the outside. As a result, the noise of the rotating electric machine (front MG 100F) can be suppressed. In addition, the non-contact portion 1p moderates the stress concentration of the fixing portion, and thus even if the fixing portion is not made strong, the inner housing 1i can be manufactured to be light and inexpensive.

[0054] Further, if at least one non-contact portion 1p is provided, a noise suppression effect can be obtained, but if a plurality of non-contact portions 1p are provided, a noise suppression effect can be more significantly obtained. However, the fixing portion is a portion for fixing the inner housing 1i and the outer housing 1o, and thus if the total length of the plurality of non-contact portions 1p is too large, the two cannot be fixed strongly. In addition, although depending on the respective lengths of the non-contact portions 1p, if the arrangement of the plurality of non-contact portions 1p is shifted, the inner housing 1i and the outer housing 1o cannot be fixed strongly. Therefore, the lengths and arrangement of the non-contact portions 1p are determined in a manner that does not interfere with the fixing of the inner housing 1i and the outer housing 1o.

[0055] In addition, in the present embodiment, the positions of the non-contact portions 1p on the one end side of the housing 1 correspond to the positions of the bolts 5 on the other end side. More specifically, as viewed in the axial direction, at least one bolt 5 is arranged in each of the central angle ranges of the non-contact portions 1p. Figure 4 The flange 1f of the inner housing 1i and the bolt insertion hole 1h (the flange 1d of the outer housing 1o and the bolt hole 1e) are shown by broken lines. Figure 4 As shown, the bolts 5 (the bolt insertion hole 1h, the bolt hole 1e) are arranged in each of the central angle ranges of the non-contact portions 1p. In other words, the positions of the non-contact portions 1p are determined in correspondence with the fastening positions of the bolts 5 on the one end of the housing 1. With respect to the central angle ranges on the right and left sides in Figure 4 With respect to the central angle ranges on the right and left sides in

[0056] Next, the reasons therefor will be described with reference to Figure 5A and Figure 5B Figure 5A and Figure 5B ​The annular 0th vibration mode of the inner housing 1i and the stator 2 integrated therewith is schematically shown. Furthermore, the annular nth vibration will be described later. If we consider the vibration of radial expansion and contraction of the cylindrical component, then the circumferential expansion or contraction vibration mode of the cylindrical component is the annular 0th vibration mode. Moreover, Figure 5A The vibration mode (antiphase vibration) is shown, where the phase of the vibration at one end of the axial direction of the housing 1 is different from the phase of the vibration at the other end. Figure 5B The vibration mode shown is a vibration mode in which the phase of the vibration at one end of the housing 1 is the same as the phase of the vibration at the other end (coordinate phase vibration).

[0057] about Figure 5A The opposite-phase vibrations shown expand at one end and contract at the other, thus compensating for the pressure fluctuations inside housing 1. On the other hand, regarding... Figure 5B The same-phase vibrations shown expand (or contract) simultaneously at both ends, thus facilitating pressure changes inside the housing 1. Consequently, the noise of the latter's same-phase vibration mode increases. If the same-phase vibrations can be effectively suppressed, the noise can be effectively suppressed. Therefore, in this embodiment, a non-contact portion 1p is formed at one end of the housing 1, and the transmission of vibration is suppressed by utilizing the gap in the non-contact portion 1p. While the fastening portion of the bolt 5 at the other end of the housing 1 cannot suppress the transmission of vibration from the inner housing 1i to the outer housing 1o, the non-contact portion 1p at one end can suppress the transmission of vibration. As a result, the propagation of noise can be effectively suppressed under the aforementioned same-phase vibration mode. That is, the radiated sound from the housing 1 can be reduced.

[0058] As described above, the front MG 100F also includes a front gear unit 101F. The housing of the front gear unit 101F is integrally formed with the outer housing 1o on the axially fixed portion (fixed range X) side (in this embodiment, it is integrally molded). The center O1 of the output shaft (drive shaft DS) of the front gear unit 101F is parallel to but not aligned with the center O of the rotation shaft of the front MG 100F. (Furthermore, regarding the rear MG 100R, described later, the center O coincides with the center O1.)

[0059] Here, as Figure 3As shown, the fixed portion (fixed range X) is divided using a first plane P1 that is perpendicular to the straight line L1 passing through the center O and the center O1 when viewed from the axial direction. Specifically, the fixed portion is divided by the first plane P1 into a first half-circumferential range R1 on the output shaft (center O1) side of the front gear unit 101F and a second half-circumferential range R2 on the opposite side of the output shaft. In this case, the total perimeter of the non-contact portions 1p within the first half-circumferential range R1 is greater than the total perimeter of the non-contact portions 1p within the second half-circumferential range R2. Furthermore, when dividing a non-contact portion 1p using the first plane P1, the perimeter of the first half-circumferential range R1 and the perimeter of the second half-circumferential range R2 are each increased by their respective division lengths.

[0060] Figure 4 The multiple non-contact portions 1p shown also satisfy this condition. The rigidity of the fixing portion is not uniform in the circumferential direction; the rigidity of the first half-circumferential range R1, which is integrally formed with the housing of the front gear unit 101F, is greater than the rigidity of the second half-circumferential range R2. Therefore, by making the total perimeter of the non-contact portions 1p within the first half-circumferential range R1 greater than the total perimeter of the non-contact portions 1p within the second half-circumferential range R2, the rigidity of the fixing portion can be ensured, and the non-contact portions 1p are adequately provided. By configuring the non-contact portions 1p in this way, the rigidity of the fixing portion can be ensured, and noise radiation can be suppressed.

[0061] Furthermore, the aforementioned rear MG 100R also has essentially the same construction as the front MG 100F. Identical structures are labeled with the same reference numerals. That is, as... Figure 6 and Figure 7 As shown, the rear MG 100R also has a housing 1 with a double-tube structure consisting of an outer shell 1o and an inner shell 1i. Furthermore, a coolant flow path is formed between the outer shell 1o and the inner shell 1i. Regarding the rear MG 100R, one end of the inner shell 1i is fixed to the outer shell 1o by press-fitting (or sintering), and the other end of the inner shell 1i is fixed to the outer shell 1o by bolt fastening. Bolt fastening is performed using a bolt insertion hole 1h formed in the flange 1f of the inner shell 1i and a bolt hole (1e) formed in the flange 1d of the outer shell 1o.

[0062] The rear MG 100R also integrally has a rear gear unit 101R. The rear gear unit 101R is located on the left side of the rear MG 100R. The rotational axis (center O) of the rear MG 100R coincides with the output shaft (center Ol) of the rear gear unit 101R. Inside the rear gear unit 101R, a planetary gear set as a reduction gear unit is housed. The rotational axis of the rear MG 100R is a hollow shaft, and is directly connected to a cylindrical sun gear of the planetary gear set. A ring gear of the planetary gear set is fixed to the inner surface of the housing of the rear gear unit 101R.

[0063] The output of the rear MG 100R input to the sun gear is output from the planetary carrier. A differential gear is also assembled to the planetary carrier. The output shaft of the planetary carrier is further led to the opposite side through the inside of the cylindrical sun gear and the hollow rotational axis of the rear MG 100R. Therefore, even if the rear MG 100R and the rear gear unit 101R are arranged on the same shaft, both ends of the output shaft of the rear gear unit 101R are respectively mechanically connected to the left and right rear wheels RW via the drive shaft DS.

[0064] Regarding the housing 1 of the rear MG 100R, one end of the inner housing li is also fixed to the outer housing lo by press-fitting (or shrink-fitting). Also, a non-contact portion lp is similarly formed at this fixed portion. In addition, the other end of the inner housing li is fixed to the outer housing lo by bolt fastening. Also, at least one bolt 5 is arranged in each of the central angular ranges of the non-contact portions lp as viewed in the axial direction. A flange ld (refer to Figure 6 ) is formed at the other end of the outer housing lo for the purpose of bolt fastening, and a flange lf (refer to Figure 6 and Figure 7 ) is formed at the other end of the inner housing li. A bolt insertion hole lh is formed in the flange lf. Furthermore, Figure 7 is a side view of the housing 1 (the outer housing lo and the inner housing li) as viewed in the axial direction of the rotational axis from the right side of the vehicle V. In this view, Figure 7 shows the stator 2, the rotor 3, and the cover lt.

[0065] In addition, regarding the rear MG 100R, the above-described effects based on the non-contact portions lp are also similarly brought about as with the above-described front MG 100F. That is, by forming the non-contact portions lp, it is possible to suppress the vibration itself of the inner housing li (and the stator 2 which is integrated by shrink-fitting), and it is possible to suppress the propagation and radiation of sound to the outside due to the vibration. As a result, it is possible to suppress the noise of the rotary electric machine (the rear MG 100R). In addition, the positions of the non-contact portions lp on the one end side of the housing 1 correspond to the positions of the bolts 5 on the other end side. Therefore, it is possible to effectively suppress the propagation of noise based on the same phase vibration mode. That is, it is possible to weaken the radiated sound from the housing 1.

[0066] AsFigure 7 The rear MG 100R also has a control unit 102R, as shown. The control unit 102R controls the operation of the rear MG 100R. The control unit 102R is fixed to the case 1 via a mounting boss 1r (see FIG. 2) formed in the case 1. Figure 6 In addition, the control unit 102R is fixed to the case 1 via a mounting boss 1r (see FIG. 2) formed in the case 1. Figure 7 The positions of the non-contact portions 1p of the fixing portions (fixing ranges X) provided between the inner case 1i and the outer case 1o by press-fitting or shrink fitting are shown in FIG. 3. With regard to the rear MG 100R, the non-contact portions 1p are formed at three locations in the circumferential direction in the fixing portions.

[0067] Here, the fixing portions (fixing ranges X) are divided in the circumferential direction by a second plane P2 passing through the center O of the rotation axis in parallel with the mounting reference surface PS of the control unit 102R, as viewed in the axial direction. Specifically, the fixing portions are divided into a third semicircular range R3 on the control unit 102R side and a fourth semicircular range R4 on the opposite side of the control unit 102R. In this case, the total length of the non-contact portions 1p in the third semicircular range R3 is greater than the total length of the non-contact portions 1p in the fourth semicircular range R4.

[0068] In addition, the mounting reference surface PS of the control unit 102R can be defined in accordance with the mounting surface of the mounting boss 1r described above. The rigidity of the fixing portions is not uniform in the circumferential direction, and the rigidity of the third semicircular range R3 in which the control unit 102R is integrated is greater than the rigidity of the fourth semicircular range R4. Therefore, the total length of the non-contact portions 1p in the third semicircular range R3 is made greater than the total length of the non-contact portions 1p in the fourth semicircular range R4, so that the rigidity of the fixing portions can be ensured, and the emission of noise can be suppressed by providing the non-contact portions 1p sufficiently. By thus configuring the non-contact portions 1p, the rigidity of the fixing portions can be ensured and the emission of noise can be suppressed.

[0069] In addition, in the present embodiment, the control unit 102R is mounted to the case 1 of the rear MG 100R, but a portion of the case of the control unit 102R can also be integrated with the case 1 of the rear MG 100R. For example, the lower half of the case of the control unit 102R can be integrated with the case 1 of the rear MG 100R, so that the upper half of the case of the control unit 102R is formed as a cover.

[0070] With regard to the vibration mode that expands and contracts in the radial direction of the cylindrical member, reference has been made to Figure 5A and Figure 5B the vibration mode of the circular ring 0th order has been described. Here, the vibration mode of the circular ring nth order (n≥0) including the circular ring 0th order will be described briefly. Figure 8A through Figure 8FThe vibration modes of the circular ring 0th~the circular ring 5thare schematically shown in FIG. 6. With respect to each vibration mode, the deformation shown by the broken line and the deformation shown by the one-dot chain line are alternately generated with respect to the reference circle S. With respect to the circular ring vibration of the actual cylindrical member, such circular ring nthvibration modes are complexly generated.

[0071] For example, if the non-contact portion Ip is provided at four portions uniformly in the circumferential direction at one end in the axial direction of the case 1, the contact portion is formed at the four portions. In this case, the circular ring vibration is restrained by the contact portion, and the vibration mode of the circular ring 4this generated as shown in FIG. 7. Also, the vibration mode of the circular ring 2ndis generated (2 is a divisor of 4). Alternatively, if the non-contact portion Ip is provided at six portions uniformly in the circumferential direction at one end in the axial direction of the case 1, the contact portion is formed at the six portions. In this case, the vibration mode of the circular ring 6this generated. Also, the vibration modes of the circular ring 2ndand the circular ring 3rdare generated (2 and 3 are divisors of 6). Figure 8E

[0072] Further, the case where the non-contact portion Ip (contact portion) is provided uniformly in the circumferential direction is described as an example, but even if the non-contact portion Ip is not provided uniformly in the circumferential direction, the number of the non-contact portion Ip is related to the number of times of vibration. The circular ring vibration modes generated at the same time cause each other to amplify. Therefore, in order to suppress such amplification, it is preferable that the number of the above-described non-contact portion Ip be a prime number. The divisors of a prime number have only 1 and itself, and thus the above-described amplification can be suppressed. That is, by setting the number of the non-contact portion Ip to a prime number, it is possible to more effectively suppress the radiation of noise. In the present embodiment, as shown in FIG. 6, with respect to the front MG 100F, the number of the non-contact portion Ip is five, and as shown in FIG. 7, with respect to the rear MG 100R, the number of the non-contact portion Ip is three (in each of these cases, a prime number). Figure 4 Figure 7

[0073] In addition, with respect to the above-described circular ring vibration modes, vibration of a lower number of times is also generated in a low frequency band. As the frequency changes from a lower value to a higher value, the circular ring nthvibration is generated in the following order. Circular ring 1st, circular ring 2nd, circular ring 3rd, circular ring 4th, circular ring 0th, circular ring 5th, circular ring 6th... According to the above-described circular ring vibration modes, the circular ring 0thvibration is generated in the low frequency band. The circular ring 0thvibration is a vibration mode in which the entire circular ring is deformed in the same direction. The circular ring 1stvibration is a vibration mode in which the circular ring is deformed in the opposite direction at the center portion of the circular ring. The circular ring 2ndvibration is a vibration mode in which the circular ring is deformed in the same direction at the center portion of the circular ring. The circular ring 3rdvibration is a vibration mode in which the circular ring is deformed in the opposite direction at the center portion of the circular ring. The circular ring 4thvibration is a vibration mode in which the circular ring is deformed in the same direction at the center portion of the circular ring. The circular ring 5thvibration is a vibration mode in which the circular ring is deformed in the opposite direction at the center portion of the circular ring. The circular ring 6thvibration is a vibration mode in which the circular ring is deformed in the same direction at the center portion of the circular ring. Figure 8A through Figure 8E It is also known that the amplitude of the vibration of a lower number of times (particularly, the circular ring 2ndand the circular ring 4th) generated in the low frequency band is large, and it is difficult to suppress the vibration. Therefore, it is preferable that the number of the non-contact portion Ip be set to be greater than or equal to five to suppress the circular ring vibration of a lower number of times. That is, it is preferable that the non-contact portion Ip be provided by a prime number of five or more. By setting the number of the non-contact portion Ip to a prime number of five or more, it is possible to more effectively suppress the radiation of noise.

[0074] ​​​Next, the preferred on-vehicle configuration of the rotary electric machines (front MG 100F and rear MG 100R) according to the present embodiment will be described. First, referring to Figs. 1A to 1C, the on-vehicle configuration (first example) taking into account vibrations when the vehicle V is running will be described. Figure 9A (Front MG 100F: left view) and Figure 9B (Rear MG 100R: right view). Figure 9A Figure 9B The tilted states of the on-vehicle front MG 100F and rear MG 100R are also shown.

[0075] Vibrations in the vertical direction are significantly generated when the vehicle V is running. Therefore, in the rotary electric machines (front MG 100F and rear MG 100R), it is preferable that the fixed portions of the inner housing 1i and the outer housing 1o obtained by press-fitting or shrink-fitting have high rigidity in the vertical direction. Here, as shown in Figs. 1A to 1C, the fixed portions (fixed range X) are divided into four ranges in the circumferential direction with reference to a horizontal plane PH and a vertical plane PV passing through the center O of the rotary shaft, as viewed in the axial direction. Figure 9A Figure 9B

[0076] The central angle of each range is 90 degrees, and the horizontal plane PH or the vertical plane PV passes through the center of each range. In this case, the total length of the non-contact portions 1p in the front quarter circumferential range RF and the rear quarter circumferential range RR is greater than the total length of the non-contact portions 1p in the upper quarter circumferential range RU and the lower quarter circumferential range RL. By thus configuring the non-contact portions 1p, the contact portions are configured to have a greater length in the vertical direction than in the upper and lower portions in the circumferential direction, and therefore the rigidity (strength) of the fixed portions with respect to vibrations in the vertical direction of the vehicle V is improved. As a result, radiation of noise can be suppressed.

[0077] ​​​The above-described vehicle-mounted configuration is an example that takes into account vibrations when the vehicle V is running. Next, an example that takes into account radiation of noise to an occupant of the vehicle V will be described (second example). If the noise that is radiated toward the occupant can be attenuated, the comfort of the occupant is improved. Here, from the axial direction, the fixed portion (fixed range X) is divided into a passenger compartment side range RP that is close to the passenger compartment PC and an opposite side range RO that is on the opposite side of the passenger compartment PC in the circumferential direction. In this case, the total length of the non-contact portion Ip in the passenger compartment side range RP is greater than the total length of the non-contact portion Ip in the opposite side range RO. By thus configuring the non-contact portion Ip, it is possible to effectively suppress noise that is radiated toward the passenger compartment PC using the non-contact portion Ip.

[0078] Here, the following describes an example of setting the passenger compartment side range RP and the opposite side range RO. First, the second A example will be described with reference to Figure 10 (left view), Figure 11A (left view), and Figure 11B (right view). As shown in Figure 10 , in the side view of the vehicle V, the outline of the passenger compartment PC is determined. The passenger compartment PC is defined by panels that form its outer shell. Specifically, the passenger compartment PC is defined using the roof panel, the front windshield, the bulkhead that separates the engine compartment, and the floor panel. Among these, considering the case where the rear space of the passenger compartment PC is continuous with the trunk, the rear end of the passenger compartment PC is vertically divided at the rear end of the last row of seat assemblies.

[0079] With respect to the passenger compartment PC thus defined, tangent lines are drawn from the center O of the rotation axis of the rotating electric machine with respect to the upper side and the lower side. With respect to the front MG 100F, the tangent line LFU on the upper side and the tangent line LFL on the lower side can be drawn. With respect to the rear MG 100R, the tangent line LRU on the upper side and the tangent line LRL on the lower side can be drawn. As shown in Figure 11A (left view), with respect to the front MG 100F, the fixed portion (fixed range X) is divided into the passenger compartment side range RP and the opposite side range RO in the circumferential direction by the tangent line LFU on the upper side and the tangent line LFL on the lower side. Of course, the range close to the passenger compartment PC is the passenger compartment side range RP.

[0080] On the other hand, as shown in Figure 11B (right view), with respect to the rear MG 100R, the fixed portion (fixed range X) is divided into the passenger compartment side range RP and the opposite side range RO in the circumferential direction by the tangent line LRU on the upper side and the tangent line LRL on the lower side. Furthermore, Figure 11A , and Figure 11BThe inclined state of the front MG 100F and the rear MG 100R mounted on the vehicle is shown. In this way, the non-contact portion Ip is disposed by setting the passenger compartment side range RP and the opposite side range RO in consideration of the space of the passenger compartment PC, so that noise radiated toward the passenger compartment PC can be effectively suppressed.

[0081] Next, with reference to Figure 12 (left view), Figure 13A (left view), and Figure 13B (right view), the second B example is described. In the above second A example, the passenger compartment PC is provided as a space, and in this example, the passenger compartment PC is represented by the center C thereof. The center C is found in accordance with the passenger compartment PC defined in the same manner as in the first example. As shown in Figure 12 , in the side view of the vehicle V, a perpendicular line is drawn at the center of the entire length 2L of the passenger compartment PC, and a horizontal line is drawn at the center of the entire height 2H of the passenger compartment PC. The intersection of the perpendicular line and the horizontal line is the center C of the passenger compartment PC.

[0082] With respect to the center C thus defined, a direction line is drawn from the center O of the rotating shaft of the rotating electric machine. With respect to the front MG 100F, a direction line LFD passing through the centers C and O can be drawn. In addition, a division surface PFD passing through the center O and perpendicular to the direction line LFD can be defined. With respect to the rear MG 100R, a direction line LRD passing through the centers C and O can be drawn. In addition, a division surface PRD passing through the center O and perpendicular to the direction line LRD can be defined.

[0083] As shown in Figure 13A (left view), with respect to the front MG 100F, the fixed portion (fixed range X) is divided into the passenger compartment side range RP and the opposite side range RO in the circumferential direction by the division surface PFD. On the other hand, as shown in Figure 13B (right view), with respect to the rear MG 100R, the fixed portion (fixed range X) is divided into the passenger compartment side range RP and the opposite side range RO in the circumferential direction by the division surface PRD. Further, Figure 13A and Figure 13B The inclined state of the front MG 100F and the rear MG 100R mounted on the vehicle is shown. In this way, the non-contact portion Ip is disposed by setting the passenger compartment side range RP and the opposite side range RO in consideration of the center C of the passenger compartment PC, so that noise radiated toward the passenger compartment PC can be effectively suppressed.

[0084] Next, with reference to Figure 14 (left view), Figure 15A (left view), and Figure 15B(Left view), the second C example will be explained. In this example, the vehicle room side range RP and the opposite side range RO are set in consideration of the position of the ear of the occupant in the vehicle room PC. In addition, the position of the ear of the driver who is a representative of the occupant is considered. However, the position of the ear of the driver cannot be uniquely determined, and therefore the uppermost point T of the seat assembly, that is, the uppermost point T of the headrest S3 is used instead of the position of the ear of the driver. In addition, the seat assembly mainly has a seat cushion S1, a seat back S2, and a headrest S3, and the heights and angles thereof can be adjusted. The uppermost point T referred to here means the position of the upper end of the headrest S3 in a state in which the headrest S3 is disposed at the highest by adjusting the height and the angle.

[0085] The adjustable sliding position of the seat assembly of the driver's seat is set to the rearmost position. The inclination angle and the height of the seat cushion S1 are set to achieve the position of the uppermost point T. The angle of the seat back S2 is also set to achieve the position of the uppermost point T, but generally the position in which the seat back S2 is most upright is considered. As for the headrest S3, the position in which the headrest S3 is most pulled out from the seat back S2 is considered, and in the case where the angle thereof can be adjusted, the angle in which the uppermost point T is achieved is set.

[0086] As shown in FIG. 6, Figure 14 in a side view of the vehicle V, a direction line is drawn from the center O of the rotation axis of the rotary electric machine with respect to the uppermost point T. As for the front MG 100F, a direction line LFT passing through the uppermost point T and the center O can be drawn. In addition, a division surface PFT passing through the center O perpendicular to the direction line LFT can be defined. As for the rear MG 100R, a direction line LRT passing through the uppermost point T and the center O can be drawn. In addition, a division surface PRT passing through the center O perpendicular to the direction line LRT can be defined.

[0087] As shown in FIG. 7, Figure 15A (Left view), as for the front MG 100F, the fixed portion (fixed range X) is divided into the vehicle room side range RP and the opposite side range RO by the division surface PFT in the circumferential direction. On the other hand, as shown in FIG. 8, Figure 15B (Right view), as for the rear MG 100R, the fixed portion (fixed range X) is divided into the vehicle room side range RP and the opposite side range RO by the division surface PRT in the circumferential direction. In addition, Figure 15A and Figure 15B the inclination states of the front MG 100F and the rear MG 100R mounted on the vehicle are shown. In this way, the vehicle room side range RP and the opposite side range RO are set in consideration of the uppermost point T and the non-contact portion 1p is disposed, and thus it is possible to effectively suppress the noise radiated toward the occupant in the vehicle room PC.

[0088] According to the above embodiment, the housing 1 has a double-pipe structure formed to create a coolant flow path inside. Here, the inner housing 1i and the outer housing 1o are fixed to each other at one end by pressing or embedding, and are fixed to each other at the other end by bolts. Moreover, in the fixing part (fixing range X) obtained by pressing or embedding, a non-contact part 1p is formed in the circumferential direction, which prevents the inner circumferential surface of the outer housing 1o from contacting the outer circumferential surface of the inner housing 1i. The non-contact part 1p can be used to suppress the outward propagation and radiation of noise caused by vibration generated in the rotating electric motor (front MG 100F or rear MG 100R).

[0089] Furthermore, when viewed axially from the rotary motor (front MG 100F or rear MG 100R), at least one bolt 5 is disposed within the respective central angle range of the non-contact portion 1p. Therefore, it is possible to suppress vibration modes in which the pressure fluctuations inside the housing 1 are large and the two ends of the axial direction vibrate in a circular motion with the same phase, thus more effectively suppressing noise.

[0090] In addition, such as Figure 3 As shown, a first half-circumference range R1 and a second half-circumference range R2 are defined based on the center O of the rotation shaft of the rotary electric motor (front MG 100F) and the center O1 of the output shaft of the front gear unit 101F. In this case, the total perimeter of the non-contact portions 1p within the first half-circumference range R1 is greater than the total perimeter of the non-contact portions 1p within the second half-circumference range R2. The housing 1 of the rotary electric motor is reinforced by the housing of the front gear unit 101F, thus the rigidity (strength) of the housing 1 is higher in the first half-circumference range R1 compared to the second half-circumference range R2. Therefore, by making the total perimeter of the non-contact portions 1p within the first half-circumference range R1 greater than the total perimeter of the non-contact portions 1p within the second half-circumference range R2, the rigidity of the fixing part can be ensured, and noise radiation can be suppressed by sufficiently providing the non-contact portions 1p.

[0091] In addition, such as Figure 7 As shown, the third half-circumference range R3 and the fourth half-circumference range R4 are defined based on the center O of the rotation shaft of the rotary motor (rear MG 100R) and the position of the control unit 102R. In this case, the total perimeter of the non-contact portions 1p within the third half-circumference range R3 is greater than the total perimeter of the non-contact portions 1p within the fourth half-circumference range R4. The housing 1 of the rotary motor is reinforced by the housing of the control unit 102R, thus the rigidity (strength) of the housing 1 is higher in the third half-circumference range R3 compared to the fourth half-circumference range R4. Therefore, by making the total perimeter of the non-contact portions 1p within the third half-circumference range R3 greater than the total perimeter of the non-contact portions 1p within the fourth half-circumference range R4, the rigidity of the fixing part can be ensured, and noise radiation is suppressed by adequately providing the non-contact portions 1p.

[0092] Furthermore, a prime number of non-contact portions 1p are provided circumferentially on the housing 1. This suppresses the amplification of the nth vibration mode of the ring. Consequently, noise radiation can be suppressed more effectively. In particular, it is preferable to provide a prime number of five or more non-contact portions 1p (see reference). Figure 4 It can suppress low-frequency circular vibrations with large amplitudes (n times), and can further effectively suppress noise radiation.

[0093] Furthermore, when the vehicle is equipped with a rotary motor (front MG 100F or rear MG 100R), such as Figure 9A and Figure 9B As shown, the upper quarter-circumference range RU, lower quarter-circumference range RL, front quarter-circumference range RF, and rear quarter-circumference range RR are defined. In this case, the total circumference of the non-contact portions 1p within the front quarter-circumference range RF and the rear quarter-circumference range RR is greater than the total circumference of the non-contact portions 1p within the upper quarter-circumference range RU and the lower quarter-circumference range RL. By configuring the non-contact portions 1p in this way, contact portions (not non-contact portions 1p) with a circumference greater than the upper and lower portions in the circumferential direction are arranged on the fixed part, thus improving the rigidity (strength) of the fixed part against vibrations in the vertical direction relative to the vehicle V. As a result, noise radiation can be suppressed.

[0094] Furthermore, when the vehicle is equipped with a rotary motor (front MG 100F or rear MG 100R), such as Figure 11A and Figure 11B As shown, the passenger compartment side range RP and the opposite side range RO are defined based on the position of the center O of the rotating shaft of the rotary motor. In this case, the total perimeter of the non-contact portions 1p in the passenger compartment side range RP is greater than the total perimeter of the non-contact portions 1p in the opposite side range RO. By configuring the non-contact portions 1p in this way, noise radiated toward the passenger compartment PC can be effectively suppressed using the non-contact portions 1p.

[0095] Furthermore, the present invention is not limited to the embodiments described above. For example, the vehicle V described above is a four-wheel drive vehicle in which the front wheel FW can be driven by the front MG100F and the rear wheel RW can be driven by the rear MG100R. However, the vehicle V may be a vehicle with only one rotary motor (front MG100F or rear MG100R). In addition, the rotary motor may not be a motor that drives the wheels, or it may not be mounted on the vehicle.

[0096] Explanation of the label

[0097] 100F Front MG (Rotary Motor)

[0098] 101F Front Gear Unit

[0099] 100R Rear MG (Rotary Motor)

[0100] 101R rear gear unit

[0101] 102R control unit

[0102] 1 housing

[0103] 1i inner housing

[0104] 1o outer housing

[0105] 1c fixed inner peripheral portion (fixed portion by press-fitting or shrink fitting)

[0106] 1n fixed outer peripheral portion (fixed portion by press-fitting or shrink fitting)

[0107] 1d flange (bolt fastening portion)

[0108] 1e bolt hole (bolt fastening portion)

[0109] 1f flange (bolt fastening portion)

[0110] 1h bolt insertion hole (bolt fastening portion)

[0111] 1p non-contact portion

[0112] 5 bolt

[0113] O center (of a rotating shaft of a rotating electric machine)

[0114] O1 center (of an output shaft of a gear unit)

[0115] L1 straight line (passing through the center O and the center O1)

[0116] P1 first plane

[0117] R1 first half circumferential range

[0118] R2 second half circumferential range

[0119] P2 second plane

[0120] R3 third half circumferential range

[0121] R4 fourth half circumferential range

[0122] RU upper quarter circumferential range

[0123] RL lower quarter circumferential range

[0124] RF front quarter circumferential range

[0125] RR rear quarter circumferential range

[0126] PC passenger compartment

[0127] RP passenger compartment side range

[0128] RO opposite side range

[0129] V vehicle

Claims

1. A rotary electric motor, wherein, The rotary motor has: Cylindrical outer shell; and A cylindrical inner shell is disposed inside the outer shell, forming a coolant flow path between the inner shell and the outer shell. The inner housing is fixed to the outer housing by pressing or burning into one end of the rotating shaft housed within the inner housing, and is fastened to the outer housing by a plurality of bolts at the other end of the rotating shaft. The fixing portions of the outer shell and the inner shell, obtained by pressing or burning, have one or more non-contact portions formed in the circumferential direction, which prevent the inner circumferential surface of the outer shell from contacting the outer circumferential surface of the inner shell. Viewed from the axial direction, at least one of the bolts is disposed within the respective central angle range of the non-contact portions.

2. The rotary motor according to claim 1, wherein, The rotary motor also includes a gear unit that reduces the output of the rotary motor. The housing of the gear unit is integrated with the outer shell. The output shaft of the gear unit is not aligned with the rotation shaft of the rotary motor, but is parallel to it. Viewed from the axial direction, when the fixed portion is divided into a first half-circumference on the output shaft side and a second half-circumference on the opposite side of the output shaft by a first plane that is perpendicular to a straight line passing through the center of the rotation shaft and the center of the output shaft, the total perimeter of the non-contact portion within the first half-circumference is greater than the total perimeter of the non-contact portion within the second half-circumference.

3. The rotary motor according to claim 1 or 2, wherein, The rotary motor also has a control unit for controlling the rotary motor. The control unit is fixed to the outer casing. Viewed from the axial direction, when the fixed portion is divided into a third half-circumference range on the side of the control unit and a fourth half-circumference range on the opposite side of the control unit by a second plane that is parallel to the mounting reference plane of the control unit and passes through the center of the rotation axis, the total circumference of the non-contact portion in the third half-circumference range is greater than the total circumference of the non-contact portion in the fourth half-circumference range.

4. The rotary motor according to claim 1 or 2, wherein, The non-contact part has a prime number of parts arranged in the circumferential direction.

5. The rotary motor according to claim 4, wherein, The non-contact part is provided with five or more parts.

6. A vehicle-mounted structure for a rotary electric motor, wherein the rotary electric motor is the rotary electric motor according to claim 1 or 2, wherein, When mounted on a vehicle, viewed from the axial direction, if the fixed portion is divided into an upper quarter-circumference range, a lower quarter-circumference range, a front quarter-circumference range, and a rear quarter-circumference range with a central angle of 90 degrees along the circumference using a horizontal and vertical plane passing through the center of the rotation axis as references, the total circumference of the non-contact portion in the front quarter-circumference range and the rear quarter-circumference range is greater than the total circumference of the non-contact portion in the upper quarter-circumference range and the lower quarter-circumference range.

7. A vehicle-mounted structure for a rotary electric motor, wherein the rotary electric motor is the rotary electric motor according to claim 1 or 2, wherein, When mounted on a vehicle, viewed from the axial direction, if the fixed portion is divided circumferentially into a vehicle compartment side region close to the vehicle compartment and an opposite side region on the opposite side of the vehicle compartment, the total perimeter of the non-contact portion in the vehicle compartment side region is greater than the total perimeter of the non-contact portion in the opposite side region.

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