Rotating electrical machine

Abstract

The present application relates to a rotating electric machine, and aims to obtain a rotating electric machine capable of mitigating the inward pouring of a frame inner cylindrical portion at an axial end portion of a core and capable of suppressing the inclination of a flange portion provided at the end portion of the frame. The rotating electric machine of the present application includes: a rotor; a cylindrical stator configured to surround the outer periphery of the rotor; a frame having a stator support portion, a flange portion, and a thick wall portion, the stator support portion being provided at the outer periphery side of the stator, the inner diameter of the stator support portion gradually increasing from the axial center portion toward the axial end portion, the flange portion being provided at one axial end portion and extending to the radially outer side, and the thick wall portion being formed across the one axial end portion of the stator; and a housing supporting the frame from the outer periphery and fixing the frame in combination with the flange portion.

Description

Technical Field

[0001] This application relates to a rotary electric motor. Background Technology

[0002] As a structure encompassing a motor, generator, or electrogenerator, a rotating electrical machine sometimes employs a method of integrating the stator into the frame internally using methods such as press-fitting or heat-fitting. The frame, integrated with the stator in this manner, can then be threaded onto the rotating electrical machine's housing. Because the stator and frame can be standardized regardless of variations in the shape of the rotating electrical machine's housing, the rotating electrical machine can be manufactured efficiently. Furthermore, a flow path for cooling material can be provided in the space between the rotating electrical machine's housing and the frame.

[0003] When fixing the stator of a rotary motor to the frame, it is necessary to prevent misalignment due to the torque reaction force of the rotor during rotation. Furthermore, when installed in a vehicle, it must withstand the acceleration and vibration exerted by the vehicle during operation. Additionally, it is necessary to prevent detachment due to impacts caused by vehicle collisions. Therefore, the stator is pressed into the frame with an appropriate interference fit.

[0004] When the stator is fixed to the frame, compressive stress from the frame surrounding the stator is applied to the stator core, causing deformation of the core. The axially stacked electromagnetic steel plates used in the core will deform, resulting in a decrease in magnetic reactance and losses. In addition, large out-of-plane deformations may occur at the two end faces of the core in the axial direction.

[0005] To mitigate the deformation of the stator core caused by compressive stress from the frame, a method of varying the inner diameter of the frame is proposed. At the axial center of the frame, a smaller inner diameter is used to maintain a larger interference fit in the core, while at the two axial end faces, a larger inner diameter is used to reduce the interference fit in the core. A technique is disclosed that, through the above-described method, reduces the compressive stress generated at the axial end faces of the core, thereby mitigating the deformation of the electromagnetic steel sheet (e.g., Patent Document 1). Existing technical documents Patent documents

[0006] Patent Document 1: Japanese Patent Application Publication No. 2021-158875 Summary of the Invention The technical problem that the invention aims to solve

[0007] For the purpose of protecting the coil wound around the stator core, the frame for fixing the stator is configured to be longer axially than the axial length of the stator and the axial length of the core on which the coil is wound. In the rotary electric machine described in Patent Document 1, the interference at the axial ends is smaller than the interference applied by the frame to the axial center of the core. Therefore, the compressive stress on the core at the axial ends is reduced, the deformation of the electromagnetic steel plate is mitigated, and the aggravation of losses can be prevented.

[0008] However, because the axial length of the frame is longer than the axial length of the core, the inner cylinder of the frame tends to tilt inwards towards the inner diameter at the axial end of the core. This tilting of the inner cylinder also causes the flange at the frame end to tilt. The flange at the frame end is designed to be fixed to the housing of the rotating electric motor, and is secured to the housing by threads. This tilt creates a gap between the flange and the mounting surface of the housing. This gap can lead to problems such as the screws securing the flange to the housing not being tightened sufficiently or becoming loose.

[0009] This application was developed to solve the aforementioned problems, and its purpose is to provide a rotary motor capable of mitigating the inward tilting of the inner cylinder portion of the frame at the axial end of the iron core towards the inner diameter side, and suppressing the tilting of the flange portion formed at the end of the frame. It can suppress the tilting of the flange portion, prevent the formation of a fixed gap between the frame and the housing, and prevent the loosening of the fixing screws. Technical solutions adopted to solve technical problems

[0010] The rotary motor of this application includes: Rotor; A cylindrical stator configured to surround the outer periphery of a rotor; A frame having a stator support portion, a flange portion, and a thick-walled portion, the stator support portion being disposed on the outer periphery of the stator, the inner diameter of the stator support portion gradually increasing from the axial center portion toward the axial end portion, the flange portion being disposed at one axial end portion and extending radially outward, and the thick-walled portion being formed across one axial end portion of the stator; and The housing supports the frame from the outer periphery and is fixed to the frame by engaging with the flange portion. Invention Effects

[0011] According to the rotary motor of this application, a rotary motor can be obtained that can alleviate the inward tilting of the inner cylinder portion of the frame at the axial end of the iron core towards the inner diameter side, and can suppress the tilting of the flange portion formed at the end of the frame. Therefore, the tilting of the flange portion can be suppressed, the generation of a fixing gap between the frame and the housing can be prevented, the loosening of the fixing screws can be prevented, and the reliability of the rotary motor can be improved. Attached Figure Description

[0012] Figure 1 This is a cross-sectional view of the rotary motor according to Embodiment 1. Figure 2 This is a cross-sectional view of the frame on which the stator of the rotary electric motor of Embodiment 1 is fixed. Figure 3 This is a cross-sectional view of the frame before the stator of the rotary motor in Embodiment 1 is fixed. Figure 4 This is a cross-sectional view of the frame after the stator of the rotary electric machine of the first comparative example is fixed. Figure 5 This is a cross-sectional view of the frame after the stator of the rotary electric machine of the second comparative example is fixed. Figure 6 This is a cross-sectional view of the frame after the stator of the rotary motor in Embodiment 1 is fixed. Figure 7 This is a cross-sectional view of the frame before the stator of the rotary motor in Embodiment 2 is fixed. Symbol Explanation 1 Rotor; 2 Stator; 3 Housing; 6 Cooling medium flow path; 10 Iron core; 12, 12a Frame; 13, 13a Flange; 14 O-ring; 16 Protrusion; 20 Stator support; 20a Axial central part of stator support; 20b Axial end of stator support; 21, 21a Thick-walled part; 50 Rotary motor. Detailed Implementation

[0013] Hereinafter, embodiments of the present application will be described with reference to the accompanying drawings.

[0014] 1. Implementation Method 1 <Structure of Rotary Electrical Machines> Figure 1 This is a cross-sectional view of the rotary motor 50 according to Embodiment 1. Figure 1 The basic structure of a rotary electric motor 50 is shown. The rotary electric motor 50 includes a rotor 1 and a stator 2. The shaft 7 of the rotor 1 is held in place by a housing 3 that forms the casing of the rotary electric motor 50 and bearings 5 ​​disposed on a cover 4. The bearings 5 ​​are positioned at the axial center of the housing 3 and the cover 4, and the rotor 1 is held opposite the stator 2 in a rotatable manner. Inside the iron core of the rotor 1, a plurality of permanent magnets are embedded at predetermined intervals in the circumferential direction. Rotational torque is provided to the outside via the shaft 7 fixed to the center of the rotor 1, or rotational torque is applied to the rotor 1 from the outside.

[0015] Furthermore, rotor 1 is not limited to a permanent magnet type rotor as described above; a wound rotor or the like can also be used. A so-called squirrel-cage rotor can also be used, in which the uninsulated rotor conductors are housed in slots in the rotor core, and short-circuited on both sides by short-circuit rings. Additionally, a wound rotor, which has slots for the stator windings to be formed in the rotor core, can also be used.

[0016] <Structure of the stator> Figure 2 This is a cross-sectional view of the frame 12 of the stator 2 of the rotary electric motor 50 according to Embodiment 1, which is fixed thereon. The stator 2 includes an iron core 10, an insulating member, and a coil 11. The iron core 10 is composed of multiple axially stacked, segmented, laminated iron cores arranged circumferentially. Electromagnetic steel plates are used for the segmented, laminated iron cores.

[0017] The electromagnetic steel plates are combined with other segmented and stacked iron cores in the circumferential direction to form a ring-shaped magnetic yoke. Furthermore, the electromagnetic steel plates have pole teeth that are narrower in the circumferential direction than the magnetic yoke and protrude towards the rotor. The segmented and stacked iron cores are integrally formed by stacking electromagnetic steel plates in the axial direction and then welding, riveting, or other methods. Alternatively, the iron core 10 can be a segmented iron core formed by combining multiple segmented and stacked iron cores in a ring shape as described above, or it can be a one-piece iron core formed integrally in the circumferential direction.

[0018] A coil 11 is wound around the pole teeth of the iron core. The winding of the coil 11 can be a concentrated winding where the coil 11 is wound only on one pole tooth of the segmented stacked iron core, or it can be a distributed winding where the coil 11 is wound between multiple pole teeth of the ring combination.

[0019] For coil 11, a conductor wire with an insulating film is used. The conductor wire can be copper wire or aluminum wire. Coil 11 is insulated from the iron core 10 by the insulating film. To prevent insulation damage caused by pinholes or other defects at the film of coil 11, insulating materials such as paper and resin are sandwiched between the iron core 10 and coil 11 to ensure insulation.

[0020] The core 10 and frame 12 are assembled by pressing, heat fitting, or other methods. Since the frame 12 is longer than the axial length of the coil 11 and the core 10, insulation damage caused by peeling of the coil 11's coating can be prevented. A flange 13 is formed at one axial end of the frame 12 for fixing the frame 12 to the housing 3. The flange 13 is fixed to the housing 3 of the rotary motor 50 by means of threaded fastening or other methods.

[0021] The rotary motor 50 generates magnetic force by supplying power from the outside to the coils 11 of the stator 2. By changing the phase of the power supplied to the coils 11 over time, the magnetic force generated by the stator 2 continuously attracts and repels the magnets embedded in the rotor 1. As a result, the rotor 1 rotates, transmitting rotational torque to the shaft 7 fixed to the rotor 1.

[0022] <Flow path for cooling medium> Under power supply, stator 2 heats up due to coil resistance, etc. Stator 2 becomes high-temperature, resulting in magnetic attenuation and losses. Therefore, it needs to be cooled. Figure 1 In this example, a cooling medium flow path 6 is formed between the frame 12 and the housing 3, and the frame 12 is cooled by circulating the cooling material. By dissipating the heat of the stator 2 to the cooled frame 12, the temperature rise of the stator 2 is suppressed.

[0023] To establish a cooling medium flow path 6 between the frame 12 and the housing 3, the frame 12 is provided with a protrusion 16 and a thick-walled portion 21. Furthermore, O-rings 14 are arranged on the protrusion 16 and the thick-walled portion 21 to ensure airtightness with the housing 3. The inner diameter of the housing 3 is precisely machined relative to the outer diameter of the protrusion 16 and the outer diameter of the thick-walled portion 21 of the frame 12, so that the O-rings 14 are appropriately flattened to fill the gap between the frame 12 and the housing 3. Cooling water can be used as the cooling medium.

[0024] To ensure the flow path 6 for the cooling medium, protrusions 16 can be provided at both axial ends of the frame 12. This is because the flow path 6 for the cooling medium can be freely positioned regardless of the position of the thick-walled portion 21. Furthermore, by making the thick-walled portion 21 also serve as the protrusions 16, miniaturization and weight reduction are also facilitated.

[0025] <The Shape of the Frame> Figure 3 This is a cross-sectional view of the frame 12 before the stator 2 of the rotary electric motor 50 in Embodiment 1 is fixed. The inner diameter of the frame 12 is machined to a size with a suitable interference fit so that the stator 2 can be fixed by pressing, heat fitting, or other methods. The portion of the frame 12 that contacts the stator 2 is called the stator support portion 20. In Embodiment 1, the inner diameter of the stator support portion 20 of the frame 12 is reduced at the axial central portion 20a of the stator support portion. Furthermore, the inner diameter is increased at the axial end portion 20b of the stator support portion. In this way, the interference fit of the stator 2 core 10 relative to the frame 12 can be set such that it is larger at the axial central portion and smaller at the axial end portion. In addition, the portion of the stator support portion 20 where the interference fit changes is smoothly tapered.

[0026] Alternatively, the inner diameter can be reduced at the axial center portion 20a of the stator support section, while keeping the inner diameter constant. By setting the minimum range of the inner diameter within a specified range, the core 10 can be tightened and securely fixed over a specified length.

[0027] In the inner diameter dimension of the stator support portion 20 of the frame 12, the radius of the axial central portion 20a of the stator support portion is set to R1, and the radius of the axial end portion 20b of the stator support portion is set to R2. When the interference of the axial central portion 20a of the stator support portion relative to the core 10 is set to IF, by setting the relationship (R2-R1) < IF, it is possible to prevent the formation of gaps between the two ends of the core 10 and the frame 12. In this way, noise generated by vibration can be prevented.

[0028] Furthermore, at least one of the frames 12 opposite to the end of the stator support portion 20 in the axial direction of the core 10 is made into a thick-walled portion 21 that extends across the end of the core 10, thereby increasing its outer diameter. Additionally, the other end of the core 10 in the axial direction is made into a protrusion 16, further increasing its outer diameter. The thick-walled portion 21, the protrusion 16, and the inner diameter portion of the housing 3 form a flow path 6 for the cooling medium. O-rings 14, which function as airtight sealing members, are arranged in the thick-walled portion 21 and the protrusion 16 of the frame 12.

[0029] <First Comparative Example> Figure 4 This is a cross-sectional view of the frame 12b after the stator 2 of the rotary electric machine of the first comparative example is fixed. As the first comparative example, Figure 4 The diagram shows the state after the stator 2 is pressed in, with the inner diameter of frame 12b having the same interference fit along the entire axial direction of core 10. Due to the strong compressive stress generated at the end faces of core 10, out-of-plane deformation occurs at both end faces of the stacked electromagnetic steel plates. This deformation of core 10 leads to decreased magnetic reluctance and increased losses.

[0030] At this time, the cylindrical portion of frame 12b deforms at the end of the core 10 due to a rapid change in stress. The cylindrical portion of frame 12b tilts inward toward the inner diameter side, with the end of the core 10 as the fulcrum. As a result, the flange 13b connected to the end of the cylindrical portion of frame 12b also tilts inward. Furthermore, when the outer diameter portion of frame 12b forms a flow path 6b for cooling medium, the mounting portion of the sealing member, i.e., the O-ring 14, disposed on the protrusion 16b of frame 12b also deforms.

[0031] Figure 4 In the diagram, A4 shows the indentation angle of the cylindrical portion of the frame 12b on the flange 13b side, and A5 shows the indentation angle of the cylindrical portion at the other end. A gap is created between the flange 13b of the frame 12b and the housing 3, resulting in an angle of inclination A6. Therefore, the threaded fixing portion that secures the flange 13b to the housing 3 will deform, reducing its reliability. Furthermore, the airtightness of the cooling medium flow path 6b may also be problematic.

[0032] <Second Comparative Example> Figure 5 This is a cross-sectional view of the frame 12c after the stator 2 of the rotary electric machine of the second comparative example is fixed. As the second comparative example, Figure 5 The diagram shows the state after the stator 2 is pressed in with the interference of the inner diameter of the frame 12c at the center of the core 10 increased and the interference at the axial ends of the core 10 decreased. The inner diameter of the frame 12c at both ends is larger than its inner diameter at the center of the core 10; therefore, the compressive stress decreases smoothly from the center of the core 10 towards both ends. Thus, the compressive stress is minimized at both ends of the core 10. Furthermore, compared to the first comparative example… Figure 4 Compared to the previous case, this can reduce the deformation of the stacked electromagnetic steel plates caused by compressive stress at the axial end of the iron core 10.

[0033] However, in this case, the cylindrical portion of frame 12c will also deform at the end of the core 10 due to the rapid change in stress. The cylindrical portion of frame 12c will bend inwards towards the inner diameter with the end of the core 10 as the fulcrum. As a result, the flange 13c connected to the end of the cylindrical portion of frame 12c will also bend inwards.

[0034] Figure 5 In the diagram, A7 shows the indentation angle of the cylindrical portion of frame 12c on the flange 13c side, and A8 shows the indentation angle of the cylindrical portion at the other end. A9 shows the inclination between the flange 13c of frame 12c and the housing 3. Compared to the first comparative example... Figure 4 Compared to the previous situation, these deformations and tilts were mitigated.

[0035] The infeed angle of the cylindrical portion of frame 12c can be set to A7 < A4 and A8 < A5. Furthermore, the tilt angle of flange 13c can be set to A9 < A6. Moreover, since the deformation of the retaining portion of the O-ring 14 on the outer diameter side of the protrusion 16c of frame 12c is also mitigated, the airtightness of the O-ring 14 to the cooling medium flow path 6c can be improved. However, the infeed angles A7 and A8 of the cylindrical portion and the tilt angle A9 of the flange 13c can affect the reliability of the rotary motor.

[0036] <Formation of Thick-walled Sections> Figure 6 This is a cross-sectional view of the frame 12 after the stator 2 of the rotary motor 50 in Embodiment 1 is fixed. Figure 3 As explained, the outer diameter of the frame 12 is enlarged by providing a thick-walled portion 21 that extends across the end of the core 10 on the flange portion 13 side of the stator support portion 20.

[0037] The thick-walled portion 21 enhances the rigidity of the cylindrical portion of the frame 12 that contacts the axial end of the core 10 on the flange portion 13 side. By providing the thick-walled portion 21, the rigidity of the cylindrical portion itself is strengthened. Figure 5Compared to the second comparative example shown, it is possible to further prevent the cylindrical portion of the frame 12 from falling in. Therefore, the flange 13 is fixed to the housing 3 without gaps, improving the reliability of the rotary motor. It also prevents defects such as insufficient tightening or loosening of the screws fixing the flange 13 to the housing 3 due to gaps.

[0038] Since the flange 13 is fixed to the housing 3 without gap, no noise is generated even if the rotary motor 50 is subjected to vibration. In addition, the mounting part of the O-ring 14, which seals the cooling medium flow path 6 formed between the frame 12 and the housing 3, can prevent deformation and maintain the airtightness of the cooling medium flow path 6.

[0039] Figure 3 , Figure 6 The example shown is an example where the thick-walled portion 21 of the outer diameter of the cylindrical portion of the frame 12 is provided only on the side of the flange portion 13. However, in cases where there is a problem with the airtightness of the O-ring 14 at the axial end opposite to the flange portion 13, by providing the thick-walled portion 21 across the end of the core 10 opposite to the flange portion 13, it is possible to prevent the cylindrical portion on the opposite side from collapsing.

[0040] An example was described where a thick-walled portion 21 was provided to increase the outer diameter of the cylindrical portion of the frame 12 in order to improve the rigidity of the end of the cylindrical portion. However, ribs may also be provided in the axial direction to improve the rigidity of the end of the cylindrical portion of the frame 12. In this way, it is advantageous because it is possible to suppress the increase in weight and material costs, and to strengthen the rigidity of the cylindrical portion of the frame 12.

[0041] 2. Implementation Method Two Figure 7 This is a cross-sectional view of the frame 12a before the stator of the rotary electric machine in Embodiment 2 is fixed. The cylindrical portion of the frame 12a tends to bend towards the inner diameter side at the axial end of the stator 2 due to the pressing of the iron core 10 of the stator 2. In addition, the flange portion 13a formed at the end of the frame 12a will also be inclined accordingly.

[0042] Therefore, in the frame 12a of the rotary motor in Embodiment 2, the flange portion 13a is pre-formed to be inclined in a direction opposite to the direction in which it is inclined due to the pressing of the iron core 10. As a result, after the iron core 10 is pressed in, the flange portion 13a can be fixed to the housing 3 without gap.

[0043] Figure 7Angle A2 indicates the pre-assigned tilt angle of the flange 13a. Here, the angle between the tapered portion (the inner diameter of the gradually increasing cone at the axial end 20b of the stator support portion of the frame 12a) and the axial direction is set as A1. In the state before the core 10 is pressed in, the angle between the tapered portion (axial end 20b of the stator support portion) of the frame 12a and the flange 13a is set as A3. It can be set as A3 = 90 degrees and A1 = A2.

[0044] By setting the inclined surface of the flange 13a perpendicular to the tapered portion (axial end 20b of the stator support portion) of the frame 12a, the inclination of the flange 13a can counteract the inward tilting of the cylindrical portion of the frame 12a towards the inner diameter. This allows the flange 13a and the mounting surface of the housing 3 to remain parallel. This is because such an angular relationship would occur if the cylindrical portion of the frame 12a were subjected to stress and naturally tilted.

[0045] However, considering the rigidity of the cylindrical portion of frame 12a and the dimensions of the thick-walled portion 21a, angle A2 can be set to a different angle than angle A1. The most suitable angle can also be determined experimentally. In this case, it is not necessary to limit angle A3 to 90 degrees.

[0046] The pre-assigned tilt angle A2 of the flange portion 13a can also be adjusted according to the magnitude of the interference fit of the frame 12a at the axial end of the core 10. Furthermore, as a preferred range for the tilt angle A2 of the flange portion 13a based on the above description, in order to obtain a mitigating effect on the inward indentation of the cylindrical portion of the frame 12a towards the inner diameter, it is preferably set to a tilt angle within a range at least relative to the axial vertical surface opposite to the flange portion 13a, up to being perpendicular to the tapered portion of the frame 12a.

[0047] Thus, by pre-shaping the frame 12a in the opposite direction before pressing in the core 10, a suitable shape can be formed after the core 10 is pressed in. This eliminates the need for excessive rigidity in the thick-walled portion 21a of the frame 12a, contributing to the miniaturization and weight reduction of the frame 12a, and improving the reliability of the rotary motor. This is because it prevents unexpected deformation of the frame 12a caused by pressing in the core 10, which could lead to gaps between the flange 13a and the housing 3, and loss of airtightness in the cooling medium flow path.

[0048] Furthermore, in the examples of Embodiment 1 and Embodiment 2 described above, the formation region of the cooling medium flow path 6 formed between the frames 12, 12a and the housing 3 was described as being located in the region overlapping the iron core 10 in the axial direction. However, to improve cooling performance, the cooling medium flow path 6 may also be located further outward than the region overlapping the iron core 10. In this case, the O-ring 14 may also be positioned further outward than the region overlapping the iron core 10.

[0049] This application describes various exemplary embodiments and examples, but the various features, methods, and functions described in one or more embodiments are not limited to specific embodiments and can be applied to embodiments individually or in various combinations. Therefore, numerous modifications not illustrated are contemplated within the scope of the technology disclosed in this application. For example, these include modifications, additions, or omissions of at least one constituent element, as well as cases where at least one constituent element is extracted and combined with constituent elements of other embodiments.

Claims

1. A rotary electric motor, comprising: Rotor; A cylindrical stator configured to surround the outer periphery of the rotor; A frame having a stator support portion, a flange portion, and a thick-walled portion, the stator support portion being disposed on the outer periphery of the stator, the inner diameter of the stator support portion gradually increasing from an axial center portion toward an axial end portion, the flange portion being disposed at one axial end portion and extending radially outward, and the thick-walled portion being formed across one axial end portion of the stator; and A housing that supports the frame from its outer periphery and engages with the flange to secure the frame. Its features are, The flange portion of the frame is configured to be radially outward and inclined in the opposite direction to the axial direction relative to a surface perpendicular to the axial direction. The frame determines the following two angles in a corresponding manner: the angle at which the radially outer side of the flange is inclined in the opposite direction of the axial direction relative to the plane perpendicular to the axial direction; and the angle at which the inner diameter of the stator support portion, which gradually increases from the axial center to the axial end, is inclined relative to the axial direction.

2. The rotary motor as described in claim 1, characterized in that, The thick-walled portion of the frame extends to the flange portion.

3. The rotary motor as described in claim 1 or 2, characterized in that, The difference between the radius of the inner diameter of the axial central portion of the stator support of the frame and the radius of the inner diameter of the axial end portion is less than the interference fit between the axial central portion of the stator support and the stator.

4. The rotary motor as described in claim 1 or 2, characterized in that, The stator support portion of the frame has a uniform inner diameter portion with a constant inner diameter at its axial central portion.

5. The rotary motor as described in claim 1 or 2, characterized in that, The frame has a circumferential protrusion on the outer periphery of the stator support that supports the inner periphery of the housing.

6. The rotary electric motor as described in claim 5, characterized in that, The stator support portion of the frame has a uniform inner diameter portion with a constant inner diameter at its axial central portion. The protrusion of the frame is located on the outer periphery of the uniform inner diameter portion, closer to the axial end side.

7. The rotary motor as described in claim 5, characterized in that, The thick-walled portion of the frame also serves as at least one of the protrusions.

8. The rotary electric motor as described in claim 5, characterized in that, The protrusion of the frame is provided with a sealing member.

9. The rotary electric motor as described in claim 1 or 2, characterized in that, A flow path for cooling medium is provided between the outer periphery of the frame and the inner periphery of the housing.

10. The rotary electric motor as described in claim 1 or 2, characterized in that, The frame makes the following two angles the same: the angle at which the radially outer side of the flange is inclined in the opposite direction of the axial direction relative to a plane perpendicular to the axial direction; and the angle at which the tapered portion of the stator support is inclined relative to the axial direction.

11. A rotary electric motor, comprising: Rotor; A cylindrical stator configured to surround the outer periphery of the rotor; A frame having a stator support portion, a flange portion, and a thick-walled portion, the stator support portion being disposed on the outer periphery of the stator, the inner diameter of the stator support portion gradually increasing from an axial center portion toward an axial end portion, the flange portion being disposed at one axial end portion and extending radially outward, and the thick-walled portion being formed across one axial end portion of the stator; and A housing that supports the frame from its outer periphery and engages with the flange to secure the frame. Its features are, The stator support portion of the frame has a uniform inner diameter portion with a constant inner diameter at its axial central portion. The thick-walled portion of the frame is disposed in an area that overlaps axially with the region in the stator support portion where the inner diameter gradually increases, excluding the uniform inner diameter portion.

12. The rotary electric motor as claimed in claim 11, characterized in that, A sealing member for sealing with the housing is provided on the outer periphery of the stator support portion of the frame and in the region corresponding to both ends of the stator axial direction.

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