CN117353493A

CN117353493A - Power module

Info

Publication number: CN117353493A
Application number: CN202210748741.2A
Authority: CN
Inventors: 裘华潮
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2022-06-28
Filing date: 2022-06-28
Publication date: 2024-01-05

Abstract

The application discloses power module, it includes motor and transmission, the motor has rotor, stator, and casing, transmission includes the anti-torsion install the radial inboard of rotor transmission shaft and installs the transmission part on the transmission shaft, transmission still includes: the two stop parts are arranged on the periphery of the transmission shaft and are respectively positioned at two axial sides of the transmission part, and an axial gap is reserved between each stop part and the transmission part; and two elastic washers respectively corresponding to the two axial gaps, wherein each elastic washer is installed in the axial gaps in a compression mode that two axial sides of the elastic washer respectively press the transmission part and the stop part through the radial two ends of the elastic washer. The power module of this application to solve the epaxial dynamic axial clearance's of transmission problem, reduced power module's noise.

Description

Power module

Technical Field

The application relates to the technical field of motors, in particular to a power module.

Background

Currently, in the output device of the motor, a transmission gear is generally used as a torque transmission member on the motor shaft. Referring to fig. 1, the motor 900 includes a motor shaft 910, and a bevel gear 920, a bearing 930, and a snap ring 940 mounted on the periphery of the motor shaft 910, wherein the bevel gear 920 is axially stopped by the bearing 930 and the snap ring 940. In view of the machining tolerances of the above components and ease of assembly, an axial gap is required between the bevel gear 920 and the bearing 930 and the snap ring 940. However, in actual operation, the motor shaft 910 inevitably changes the transmission direction of the torque according to the actual working condition. At this time, the direction of the axial force of the bevel gear 920 also changes, and the bevel gear 920 also moves back and forth in the axial direction. For example, the position where the snap ring 940 is pressed is moved to the position where the inner ring of the bearing 930 is pressed, or the position where the inner ring of the bearing 930 is pressed is moved to the position where the snap ring 940 is pressed. In this case, the axial gap 901 is dynamically formed between the helical gear 920 and the bearing 930 or between the helical gear 920 and the snap ring 940; meanwhile, the bevel gear 920 may collide or collide with the bearing 930 or the snap ring 940, which not only generates noise, but also may cause abrasion damage to the bevel gear 920, the bearing 930 and the snap ring 940, thereby affecting the service life and reliability of the motor as a whole.

Thus, there is a need to design a power module to solve the above-mentioned problems.

Disclosure of Invention

The application provides a power module to solve the problem of dynamic axial clearance on a transmission shaft.

To achieve the above object, a power module includes a motor having a rotor, a stator located radially outside the rotor, and a housing fixed radially outside the stator, and a transmission device including a transmission shaft torsionally mounted radially inside the rotor and a transmission member mounted on the transmission shaft and disposed at a distance from the rotor, the transmission device further including:

the two stop parts are arranged on the periphery of the transmission shaft and are respectively positioned at two axial sides of the transmission part, and an axial gap is reserved between each stop part and the transmission part; the method comprises the steps of,

the two elastic washers respectively correspond to the two axial gaps, and each elastic washer is installed in the axial gaps in a compression mode that the two axial sides of the elastic washer respectively press the transmission part and the stop part through the two radial ends of the elastic washer.

Optionally, in some embodiments of the present application, the elastic washer extends from a radially inner side of the power module toward a radially outer side of the power module while extending in an axial direction of the power module.

Alternatively, in some embodiments of the present application, the resilient gasket is a tapered gasket or a bowl-shaped gasket.

Optionally, in some embodiments of the present application, a radially outer section of an axial one side surface of the elastic washer is a first arcuate convex surface, and a radially inner section of an axial other side surface is a second arcuate convex surface;

wherein one of the first arcuate convex surface and the second arcuate convex surface abuts against the transmission member, and the other of the first arcuate convex surface and the second arcuate convex surface abuts against the stopper member.

Optionally, in some embodiments of the present application, the elastic washer has a first state, a second state, and a third state in which deformation amounts sequentially increase;

the first arc-shaped convex surface and the second arc-shaped convex surface comprise a first section, a second section and a third section which are sequentially connected from the radial inner side to the radial outer side of the elastic gasket;

when the elastic washer is in the first state, the third section of the first arc-shaped convex surface presses against one of the transmission component and the stop component, and the first section of the second arc-shaped convex surface presses against the other of the transmission component and the stop component;

when the elastic washer is in the second state, the second section of the first arc-shaped convex surface presses against one of the transmission component and the stop component, and the second section of the second arc-shaped convex surface presses against the other of the transmission component and the stop component;

when the elastic washer is in the third state, the first section of the first arc-shaped convex surface abuts against one of the transmission member and the stop member, and the third section of the second arc-shaped convex surface abuts against the other of the transmission member and the stop member.

Optionally, in some embodiments of the present application, a radially inner end of the elastic washer is formed with a central hole, and an inner circumferential surface of the central hole is a cylindrical surface.

Optionally, in some embodiments of the present application, the material of the elastic washer is spring steel.

Optionally, in some embodiments of the present application, the drive shaft is further mounted radially inward of the housing by means of a first bearing and a second bearing, wherein:

the first bearing is located between the rotor and the transmission part and is configured as one of the stop parts;

the second bearing is located on a bearing side of the rotor remote from the first bearing.

Optionally, in some embodiments of the present application, the other of the stop members is a snap ring.

Optionally, in some embodiments of the present application, the first bearing is a rolling bearing.

Compared with the prior art, the power module has the advantages that the two elastic washers are arranged on the two sides of the axial direction of the transmission part, so that the problem of dynamic axial clearance on the transmission shaft can be solved, the noise of the power module is reduced, and the NVH (noise, vibration and harshness) of the motor is improved.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings that are needed in the description of the embodiments will be briefly introduced below, it being obvious that the drawings in the following description are only some embodiments of the present application, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

Fig. 1 is a schematic diagram of an output device of a conventional motor.

Fig. 2 is a schematic diagram of a power module provided in an embodiment of the present application.

Fig. 3 is an illustration of a first embodiment of a transmission provided in an embodiment of the present application.

Fig. 4 is a schematic diagram of an operation state of an elastic washer in a transmission device according to an embodiment of the present application.

Fig. 5 is a schematic diagram II of the working state of the elastic washer in the transmission device according to the embodiment of the present application.

Fig. 6 is a schematic diagram III of an operating state of an elastic washer in the transmission device according to the embodiment of the present application.

Fig. 7 is a partial schematic view of an elastic washer provided in an embodiment of the present application.

Fig. 8 is an illustration of a second embodiment of a transmission provided in an embodiment of the present application.

The main reference numerals in the drawings of the present specification are explained as follows:

200. 900 motor 230 shell

100. Transmission 220 stator

10. Transmission shaft 210 rotor

20. Axial one side surface of the transmission member 41

30. The other axial side surface of the stopper member 42

30a first stop member 411 first arcuate convex surface

30b first stop member 412 first extension surface

40. Second arc convex surface of elastic washer 421

40a first resilient washer 422 second extension surface

40b second spring washer 401 center hole

4111. 4211 first segment 910 motor shaft

4112. 4212 second segment 920 helical gear

4113. 4213 third segment 930 bearing

940. Clasp 11 first bearing

12. Second bearing

Detailed Description

The following description of the embodiments of the present application will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all, of the embodiments of the present application. All other embodiments, based on the embodiments herein, which are within the scope of the protection of the present application, will be within the skill of the art without inventive effort.

In the description of the present application, it should be understood that the terms "center," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," and the like indicate orientations or positional relationships based on the orientation or positional relationships shown in the drawings, merely to facilitate description of the present application and simplify the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present application.

The terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present application, unless otherwise indicated, the meaning of "a plurality" is two or more.

In the description of the present application, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; the two components can be mechanically connected, can be directly connected or can be indirectly connected through an intermediate medium, and can be communicated with each other. The specific meaning of the terms in this application will be understood by those of ordinary skill in the art in a specific context.

As shown in fig. 2 and 3, the present application provides a power module 1 that includes a transmission 100 and a motor 200. The motor 200 has a rotor 210, a stator 220 located radially outward of the rotor 210, and a housing 230 fixed radially outward of the stator 220. The transmission 100 has a transmission shaft 10, a transmission part 20, two stop parts 30 and two elastic washers 40. The drive shaft 10 is mounted radially inward of the rotor 210. The transmission member 20 is rotatably mounted on the outer periphery of the transmission shaft 10 and is spaced apart from the rotor 210 in the axial direction of the transmission shaft 10. Two stop members 30 are disposed around the periphery of the transmission shaft 10 and on two sides of the transmission member 20 in the axial direction, and an axial gap is provided between each stop member 30 and the transmission member 20. The two elastic washers 40 respectively correspond to the two axial spaces, and each elastic washer 40 is installed in the axial gap in a compressed manner in such a way that the two axial sides of the elastic washer respectively press the transmission component 20 and the stop component 30 through the two radial ends of the elastic washer. Specifically, in the axial direction of the transmission 100, one axial side of the elastic washer 40 abuts against the transmission member 20 by its own radially inner end, while the other axial side of the elastic washer 40 abuts against the stopper member 30 by its own radially outer end; alternatively, one axial side of the elastic washer 40 is pressed against the transmission member 20 by its own radially outer end, and the other axial side of the elastic washer 40 is pressed against the stopper member 30 by its own radially inner end.

Currently, in order to solve the problem of dynamic axial play caused by axial play of the transmission component 20, a rigid snap ring or a pre-tightening elastic member (such as a diaphragm spring, a wave spring or a coil spring) is often used for axial play compensation. In the solution of the clearance compensation by using the above-mentioned rigid snap ring, a certain axial clearance is still required between the transmission member 20 and the stop member 30 to meet the assembly requirement. That is, the above-mentioned rigid snap ring can only reduce the axial gap, but cannot achieve the purpose of completely eliminating the axial gap. Furthermore, the use of the rigid snap ring is limited, and the size of the rigid snap ring needs to be designed according to the specific axial gap size, so that the manufacturing cost of the transmission device is increased. In the scheme of axial gap compensation by using the existing pre-tightening elastic member (such as a diaphragm spring, a wave spring or a coil spring), the pre-tightening elastic member is easy to be plastically deformed under the axial extrusion action of the transmission member 20 because the axial gap is smaller than or equal to 0.3mm and the axial extrusion force of the transmission member 20 is in kN level or even 10kN level, so that the pre-tightening elastic member fails and cannot play a role of buffering.

In the solution of the present application, the axial deformation of the two elastic washers 40 forms a variation trend similar to "the expansion and the contraction" in response to the axial movement of the transmission member 20, so as to overcome the dynamic variation trend of the axial gap at the two axial sides of the transmission member 20; in addition, in the above process, the two elastic washers 40 are always kept pressed against the transmission member 20 and the stopper member 30, thereby realizing a true gapless assembly. In this way, the transmission device 100 of the present application can solve the problem of dynamic axial clearance on the transmission shaft 10, and achieve zero clearance assembly in a true sense. Meanwhile, the elastic performance of the elastic washer 40 can meet the assembly requirement, and can also provide elastic buffering for the axial extrusion of the transmission component 20, so as to buffer the impact force of the transmission component 20, and further reduce or even eliminate the collision noise between the transmission component 20 and the stop component 30. In addition, the elastic performance of the elastic washer 40 enables the elastic washer 40 to be suitable for axial gaps with different sizes, and reduces the manufacturing cost of the transmission device 100.

The transmission member 20 is used for torque transmission of the propeller shaft 10. That is, the torque of the drive shaft 10 obtained at the motor 200 may be transmitted to an external device via the drive member 20, or the torque of an external device may be transmitted to the drive shaft 10 and thus to the motor 200 via the drive member 20. Further, the transmission member 20 is rotatably mounted on the outer periphery of the transmission shaft 10. In one embodiment, the driving member 20 and the driving shaft 10 are both spline-connected. For example, an internal spline is formed on the inner peripheral surface of the transmission member 20, and an external spline that mates with the internal spline is formed on the outer peripheral surface of the transmission shaft 10. The transmission part 20 and the transmission shaft 10 are connected in a torsion-resistant manner by the engagement of the internal and external splines. In particular embodiments, the transmission member 20 may be a transmission gear.

Wherein the stop member 30 may be a separate member provided for axial stop of the transmission member 20. At this time, the stopper member 30 may be a stopper clasp.

Alternatively, the stop member 30 may be a member mounted on the drive shaft 10 for supporting or connecting. For example, the stopper 30 may be a bearing mounted on the drive shaft 10 for supporting the drive shaft 10. Wherein the two stop members 30 are a first stop member 30a and a second stop member 30b, respectively. The first stop member 30a is located on one axial side of the transmission member 20 with a first axial gap from the transmission member 20. The second stop member 30b is located on the other axial side of the transmission member 20 with a second axial gap from the transmission member 20.

In particular to the present embodiment, the drive shaft 10 is also mounted radially inside the housing 230 by means of a first bearing 11 and a second bearing 12. Wherein said first bearing 11 is mounted on said drive shaft 10 between said rotor 210 and said drive member 20. The second bearing 12 is mounted on the drive shaft 10 on the bearing side of the rotor 210 remote from the first bearing 11. In a specific implementation, the first bearing 11 is a rolling bearing, and the second bearing 12 is a floating bearing.

Based on this, the first stopper member 30a is an inner ring of the first bearing 11 for supporting the drive shaft 10, and the second stopper member 30b is a snap ring. In a specific implementation, the stop collar may be a rigid collar. Based on the above embodiment, one axial end of the outer peripheral surface of the transmission shaft 10 is formed with a shoulder protruding radially outward thereof, and the shoulder is used for stopping the first stopper 30 a. At the same time, the other axial end of the outer peripheral surface of the transmission shaft 10 forms a mounting groove recessed inward in the radial direction thereof, and the second stopper member 30b is inserted and fixed in the mounting groove. Preferably, the mounting groove is an annular groove extending in the circumferential direction of the drive shaft 10.

Referring to fig. 4, the elastic washers 40 are hollow annular rings, respectively. The elastic washer 40 extends obliquely with respect to the oblique direction of the radial plane of the drive shaft 10 perpendicular to the axial direction thereof. More specifically, the elastic washer 40 extends from the radially inner side of the transmission 100 toward the radially outer side of the transmission 100 while extending in the axial direction of the transmission 100. By defining the overall extension trajectory of the elastic washer 40, it is ensured that the overall structural elasticity and rigidity of the elastic washer 40 can be simultaneously satisfied to withstand the axial compression of the transmission member 20, thus ensuring a continuous and stable operation of the elastic washer 40.

For example, referring to fig. 7, the overall extending track of the elastic washer 40 is a straight line in a cross section. The elastic washer 40 is a conical ring piece as a whole. Still further, the elastic washer 40 is implemented in the form of a conical washer. Here, it should be noted that the tapered washer is only an exemplary embodiment of the elastic washer of the present application, and the specific embodiment of the elastic washer 40 described herein is not limited thereto. In other embodiments, the overall path of extension of the elastic washer 40 may be an arc as viewed in cross-section. At this time, the elastic washer 40 may be implemented in the form of a bowl-shaped washer.

Further, the radially outer section of the axial one side surface 41 of the elastic washer 40 is formed with a first arcuate convex surface 411, and the radially inner section of the axial other side surface 42 is formed with a second arcuate convex surface 421. Wherein one of the first arc-shaped convex surface 411 and the second arc-shaped convex surface 421 is used to press the transmission member 20, and the other of the first arc-shaped convex surface 411 and the second arc-shaped convex surface 421 is used to press the stopper member 30.

Wherein the radially inner section refers to a radial section of the axial one side surface 41 or the axial other side surface 42 near the central axis of the elastic washer 40 in the radial direction of the elastic washer 40. The axial one-side surface 41 or the axial other-side surface 42 is a radial section of the elastic washer 40 away from the central axis in the radial direction.

It will be appreciated that under axial compression of the transmission member 20, the resilient gasket 40 will tip over. Thus, the contact position (or abutment position) of the elastic washer 40 for contacting the transmission member 20 or the stopper member 30 may be changed at different compression amounts. By arranging the first arc-shaped convex surface 411 and the second arc-shaped convex surface 421, the elastic gasket 40 can be ensured to contact with the adjacent parts in a surface-to-surface bonding mode all the time at different contact positions, so that a sufficient contact area between the elastic gasket 40 and the adjacent parts is ensured all the time, contact stress is reduced, and abrasion is reduced. For example, in the embodiment of the stop collar that is provided with the second stop member 30b, the arcuate convex surface may increase the bearing area of the stop collar, improve the bearing capacity of the stop collar, and prolong the service life of the stop collar.

More specifically, the first arc-shaped convex surface 411 protrudes toward one side in the axial direction of the elastic washer 40, and the second arc-shaped convex surface 421 protrudes toward the other side in the axial direction of the elastic washer 40. In addition, the first arc convex surface 411 and the second arc convex surface 421 are both smooth curved surfaces, so as to ensure smooth transition of the contact position, prevent the problem of stress concentration at a local position, and prevent damage.

With continued reference to fig. 7, a radially inner section of the axial one side surface 41 of the elastic washer 40 is formed with a first extension surface 412 connected to the first arcuate convex surface 411, and a radially outer section of the axial other side surface 42 of the elastic washer 40 is formed with a second extension surface 422 connected to the second arcuate convex surface 421. Specifically, the first extension surface 412 and the second extension surface 422 are conical ring surfaces. At this time, the extending tracks of the first extending surface 412 and the second extending surface 422 are two substantially parallel straight lines as viewed in cross section.

In yet other embodiments, the first extension surface 412 and the second extension surface 422 extend along two substantially parallel arcs. Still alternatively, the first extension surface 412 and the second extension surface 422 may have different extension trajectories. For example, the shape of the elastic washer 40 may be adaptively adjusted without changing the overall extension trajectory of the elastic washer 40, so as to adjust the elastic performance of the elastic washer 40. At this time, the elastic washer 40 may be understood as a modified form of the above-described tapered washer or bowl-shaped washer.

Referring to fig. 7, the radially inner end of the elastic washer 40 is surrounded by a central hole 401, and the inner circumferential surface 43 of the central hole 401 is a cylindrical surface. The elastic washer 40 is sleeved on the periphery of the transmission shaft 10 through the central hole 401. It will be appreciated that the inner diameter of the central bore 401 is slightly larger than the outer diameter of the drive shaft 10 during a particular installation, to facilitate assembly of the elastomeric washer 40 and the drive shaft 10 without causing radial displacement of the elastomeric washer 40. Further, the inner peripheral surface 43 is located radially inward of the axial surfaces 41, 42 of the elastic washer 40, and both axial ends of the inner peripheral surface 43 are respectively abutted with the axial surfaces 41, 42 of the elastic washer 40. More specifically, the two axial ends of the inner peripheral surface 43 are respectively adjacent to the first extension surface 412 and the second arc-shaped convex surface 421.

In a specific embodiment, the material of the elastic washer 40 may be spring steel. The spring steel has excellent comprehensive properties such as mechanical properties (especially elastic limit, strength limit and yield ratio), anti-elastic reduction performance, fatigue performance, hardenability and physicochemical properties (heat resistance, low temperature resistance, oxidation resistance, corrosion resistance and the like). However, the material of the elastic washer 40 is not limited as long as it can elastically deform in the axial direction.

In the transmission 100 of the present application, the two elastic washers 40 each have substantially three operating states, i.e., a first state (also referred to as an sprung-open state), a second state (also referred to as a precompressed state), and a third state (also referred to as an overcompressed state) in which the deformation amount sequentially increases. Wherein the second condition corresponds to a rest condition of the drive shaft 10, in which no axial force is generated by the drive member 20, both of the resilient washers 40 are in the second condition. The first state and the third state correspond to the rotation state of the transmission shaft 10, in which the transmission member 20 generates an axial force, and one of the two elastic washers 40 (i.e. subjected to the axial pressing force of the transmission member 20) is in the first state and the other is in the third state; further, when the rotation direction of the transmission shaft 10 is changed, the direction of the axial force of the transmission member 20 is changed, and thus the working states of the two elastic washers 40 are also exchanged.

Referring to fig. 7, in order to further adapt to the three working states of the elastic washer 40, the first arc-shaped convex surface 411 is formed by a first section 4111, a second section 4112 and a third section 4113 that are sequentially connected from the radially inner side to the radially outer side of the elastic washer 40; the second arcuate convex surface 421 also includes a first section 4211, a second section 4212 and a third section 4213 connected in sequence from the radially inner side toward the radially outer side of the elastic washer 40.

Referring to fig. 3, in further combination with the embodiment of the stop member 30, the two elastic washers 40 are a first elastic washer 40a located in the first axial gap and a second elastic washer 40b located in the second axial gap, respectively. Referring to fig. 5 and 7, for the first arcuate washer 40a, the first arcuate convex surface 411 faces the first stop member 30a and abuts against the first stop member 30a, and the second arcuate convex surface 421 faces the transmission member 20 and abuts against the transmission member 20. Referring to fig. 4 and 7, for the second arcuate washer 40b, the first arcuate convex surface 411 faces the transmission member 20, and the second arcuate convex surface 421 faces the second stop member 30b and abuts against the second stop member 30b.

Fig. 4 schematically shows the second state of the elastic washer 40, taking the second state of the second elastic washer 40b as an example. Fig. 5 and 6 are schematic views of the first elastic washer 40a and the second elastic washer 40b when the transmission member 20 axially presses the first stopper member 30a, respectively, wherein fig. 5 schematically illustrates the third state of the elastic washer 40 by taking the third state of the first elastic washer 40a as an example, and fig. 6 schematically illustrates the first state of the elastic washer 40 by taking the first state of the second elastic washer 40b as an example. It should be noted that, with respect to fig. 5 and 6, when the rotation direction of the transmission shaft 10 is changed, the first elastic washer 40a in fig. 5 is changed from the third state to the first state, and the second elastic washer 40b in fig. 6 is changed from the first state to the third state.

Referring to fig. 4 and fig. 7 together, when the elastic washer 40b is in the second state, the second section 4112 of the first arc-shaped convex surface 411 abuts against the transmission component 20, and the second section 4212 of the second arc-shaped convex surface 421 abuts against the second stop component 30b.

Referring to fig. 5 and 7, when the first elastic washer 40a is in the third state, the first section 4111 of the first arc-shaped convex surface 411 abuts against the first stop member 30a, and the third section 4213 of the second arc-shaped convex surface 421 abuts against the transmission member 20.

Referring to fig. 6 and 7, when the first elastic washer 40a is in the first state, the third section 4113 of the first arc-shaped convex surface 411 abuts against the first stop member 30a, and the first section 4211 of the second arc-shaped convex surface 421 abuts against the transmission member 20.

The above description has been made schematically for the case where the overall structure and the inclination direction of the two elastic washers 40 are substantially the same. It should be noted that the embodiment of the two elastic washers 40 in the transmission 100 described in the present application is not limited thereto. In a specific implementation, the two elastic washers 40 may be differently arranged on the premise of ensuring the work function of the two elastic washers 40. For example, referring to fig. 8, in some embodiments, the first elastic washer 40a and the second elastic washer 40 are conical washers, but the inclination directions of the two washers are different from the radial plane of the transmission shaft 10 perpendicular to the axial direction.

The foregoing is merely specific embodiments of the present application, but the scope of the present application is not limited thereto, and any person skilled in the art can easily think about changes or substitutions within the technical scope of the present application, and the changes and substitutions are intended to be covered by the scope of the present application. Therefore, the protection scope of the present application shall be subject to the protection scope of the claims. Furthermore, the foregoing description of the principles and embodiments of the present application has been provided for the purpose of illustrating the principles and embodiments of the present application and for the purpose of providing a simplified understanding of the principles and embodiments of the present application, and is not intended to limit the scope of the present application.

Claims

1. A power module comprising an electric machine having a rotor, a stator located radially outward of the rotor, and a housing secured radially outward of the stator, and a transmission including a drive shaft torsionally mounted radially inward of the rotor and a transmission member mounted on the drive shaft and disposed in spaced relation to the rotor, the transmission further comprising:

2. The power module of claim 1, wherein the resilient gasket extends from a radially inner side of the power module toward a radially outer side of the power module while extending in an axial direction of the power module.

3. The power module of claim 2, wherein the resilient gasket is a conical gasket or a bowl gasket.

4. The power module according to claim 1 or 2, wherein the radially outer section of one axial side surface of the elastic washer is a first arcuate convex surface, and the radially inner section of the other axial side surface is a second arcuate convex surface;

5. The power module of claim 4, wherein the elastic washer has a first state, a second state, and a third state in which the deformation amount sequentially increases;

6. The power module according to claim 1, wherein a radially inner end of the elastic washer is formed with a center hole, and an inner circumferential surface of the center hole is a cylindrical surface.

7. The power module of claim 1, wherein the resilient gasket material is spring steel.

8. The power module of claim 1, wherein the drive shaft is further mounted radially inward of the housing by a first bearing and a second bearing, wherein:

9. The power module of claim 8 wherein the other of the stop members is a snap ring.

10. The power module of claim 8, wherein the first bearing is a rolling bearing.