Noise vibration harshness reduction assembly and method, axial ring

Abstract

Noise and vibration sound roughness reduction assemblies and methods, axial rings are disclosed. The reduction assemblies include a housing, a component, and an axial ring. The component is supported via the housing and is movable relative to the housing. The axial ring is disposed axially along the component. The axial ring is configured to attenuate axial sound-induced vibrations in response to operation of the component.

Description

[0001] Cross-references to related applications

[0002] This application relates to U.S. Application No. 17 / 141,594, filed January 5, 2021, which is incorporated herein by reference in its entirety. Technical Field

[0003] Vehicles include many components that can rotate during operation. These rotating components may generate noise during operation. This noise can be heard by the occupants of the vehicle. Summary of the Invention

[0004] This disclosure provides a noise vibration harshness reduction assembly, including a housing and a component supported via the housing. The component is movable relative to the housing. The noise vibration harshness reduction assembly also includes an axial ring. The axial ring is disposed axially along the component. The axial ring is configured to attenuate axial sound-induced vibrations in response to operation of the component.

[0005] In some aspects, the component is rotatable about a central axis, and an axial ring continuously surrounds the central axis. Furthermore, in some configurations, the axial ring is axially positioned between the component and the housing relative to the central axis. Optionally, a snap-fit ​​ring engages the axial ring and the housing to retain the axial ring relative to the component.

[0006] In other aspects, the axial ring includes an axial body extending outwardly to a first and a second axially distal edge opposite to each other. Furthermore, in some configurations, the first axially distal edge is radially spaced from the second axially distal edge relative to the central axis. In various configurations, the first axially distal edge faces inwardly toward the central axis, and the second axially distal edge faces outwardly away from the central axis.

[0007] In some configurations, the axial body surrounds the central axis. Furthermore, in some configurations, the axial body extends radially outward relative to the central axis to overlap with a portion of the component.

[0008] Optionally, the axial ring includes an axial flange that protrudes away from one of the first and second axial distal edges. In one configuration, the axial flange is guided to the housing to secure the axial ring to the housing. In another configuration, the axial flange is guided to the component to secure the axial ring to the component.

[0009] In some aspects, the axial flanges further include a plurality of axial flanges spaced apart from each other. In various configurations, each of the axial flanges extends inward toward the central axis from a first axial distal edge. In other configurations, each of the axial flanges extends away from the axial body from a second axial distal edge.

[0010] In other aspects, the axial body of the axial ring includes multiple axial corrugations, and in some configurations, these axial corrugations are disposed between a first axial distal edge and a second axial distal edge. Typically, when a low load is applied axially to the bearing, these axial corrugations engage the axial side of the bearing and the axial wall of the housing to stabilize the bearing.

[0011] In various aspects, the housing defines a bore along a central axis, and the component includes a bearing disposed in that bore. For example, an axial ring is disposed axially relative to the central axis along the bearing. In some configurations, the bearing includes: a first race fixed to the housing; and a second race rotatable about a central axis relative to the first race. In some aspects, an axial body is disposed axially relative to the central axis along the first race.

[0012] Typically, the first race of a bearing includes a radial side facing away from the central axis and an axial side disposed transversely to the radial side, such that the radial and axial sides are adjacent to each other. Furthermore, the housing typically includes an axial wall facing the axial side of the bearing. Optionally, the housing includes a shoulder extending along both the radial and axial sides of the bearing. In some aspects, when a high load is applied axially to the bearing, an axial ring engages the shoulder. In other aspects, when a low load is applied axially to the bearing, an axial corrugation engages the axial side of the bearing and the axial wall of the housing to stabilize the bearing.

[0013] In some aspects, the axial side of the first race is referred to as the first axial side, and the first axial side is disposed transversely to the radial side. Furthermore, the first race of the bearing typically also includes a second axial side, which is opposite to the first axial side and disposed transversely to the radial side. Typically, the axial wall of the housing faces the first axial side of the bearing.

[0014] In some configurations, the axial ring is further defined as a first axial ring, which is axially disposed relative to the central axis between a first axial side of the first race and an axial wall of the housing. Optionally, a second axial ring is axially disposed relative to the central axis along a second axial side of the first race.

[0015] This disclosure also provides an axial ring disposed axially along the component. The axial ring is configured to attenuate axial sound-induced vibrations in response to operation of the component. The axial ring includes an axial body extending outwardly to a first and a second axially distal edge opposite to each other. The axial ring includes an axial flange projecting away from one of the first and second axially distal edges. The axial body of the axial ring includes a plurality of axial corrugations disposed between the first and second axially distal edges. The axial body is configured to attenuate axial sound-induced vibrations in response to operation of the component.

[0016] This disclosure further provides a method for attenuating axial and radial sound-induced vibrations in response to the operation of components within a housing, using axial and radial rings. The axial ring is disposed transversely to the radial ring along the component. A torque to be applied to the radial ring is selected. The stiffness of the radial ring is determined based on a stiffness-torque curve that utilizes the selected torque to attenuate radial sound in response to component operation. The stiffness of the axial ring is determined based on the axial load and the selected torque of the radial ring. A radial ring satisfying the determined stiffness of the radial ring is manufactured. An axial ring satisfying the determined stiffness of the axial ring is manufactured. The component profile is manufactured within a torque range higher than the selected torque applied to the radial ring. The axial ring is disposed axially along the component to attenuate axial sound in response to component operation.

[0017] The present invention also discloses the following technical solutions:

[0018] Solution 1. A noise, vibration, and acoustic roughness reduction component, comprising:

[0019] case;

[0020] Components, which are supported by the housing and are movable relative to the housing; and

[0021] An axial ring is disposed axially along the component, and wherein the axial ring is configured to attenuate axial sound-induced vibrations in response to operation of the component.

[0022] Option 2. The noise, vibration, and acoustic roughness reduction component according to Option 1, wherein the component is rotatable about a central axis, and the axial ring continuously surrounds the central axis.

[0023] Option 3. The noise, vibration, and acoustic roughness reduction component according to Option 2, wherein the axial ring is axially disposed between the component and the housing relative to the central axis.

[0024] Option 4. The noise, vibration, and acoustic roughness reduction component according to Option 2, wherein:

[0025] The axial ring includes an axial body that extends outwardly to a first axial distal edge and a second axial distal edge that are opposite each other;

[0026] The first axial distal edge is radially spaced from the second axial distal edge relative to the central axis; and

[0027] The first axial distal edge faces inward toward the central axis, and the second axial distal edge faces outward away from the central axis.

[0028] Option 5. The noise, vibration, and acoustic roughness reduction component according to Option 4, wherein the axial ring includes an axial flange that protrudes outward from one of the first axial distal edge and the second axial distal edge.

[0029] Option 6. The noise, vibration, and acoustic roughness reduction assembly according to Option 5, wherein the axial flange is guided to the housing to secure the axial ring to the housing.

[0030] Option 7. The noise, vibration, and acoustic roughness reduction assembly according to Option 5, wherein the axial flange is guided to the component to secure the axial ring to the component.

[0031] Option 8. The noise, vibration, and acoustic roughness reduction component according to Option 5, wherein the axial flange further comprises a plurality of axial flanges spaced apart from each other, and wherein each of the axial flanges extends inwardly toward the central axis from the first axial distal edge.

[0032] Option 9. The noise, vibration, and acoustic roughness reduction component according to Option 5, wherein the axial flange further comprises a plurality of axial flanges spaced apart from each other, and wherein each of the axial flanges extends from the second axial distal edge away from the axial body.

[0033] Solution 10. The noise, vibration, and acoustic roughness reduction component according to Solution 4, wherein the axial body of the axial ring includes a plurality of axial corrugations disposed between the first axial distal edge and the second axial distal edge.

[0034] Solution 11. The noise, vibration, and acoustic roughness reduction component according to Solution 1, wherein:

[0035] The axial ring includes an axial body surrounding a central axis; and

[0036] The axial body extends radially outward relative to the central axis to overlap with a portion of the component.

[0037] Option 12. The noise, vibration, and acoustic roughness reduction component according to Option 11, wherein the axial body of the axial ring includes a plurality of axial corrugations that overlap with a portion of the component.

[0038] Option 13. The noise, vibration, and acoustic roughness reduction component according to Option 1, wherein:

[0039] The housing defines a hole along its central axis;

[0040] The component includes a bearing disposed in the hole; and

[0041] The axial ring is arranged axially along the bearing relative to the central axis.

[0042] Option 14. The noise, vibration, and acoustic roughness reduction component according to Option 13, wherein:

[0043] The bearing includes: a first race fixed to the housing; and a second race rotatable about the central axis relative to the first race; and

[0044] The axial ring includes an axial body, which is axially disposed relative to the central axis along the first seat ring.

[0045] Option 15. The noise, vibration, and acoustic roughness reduction component according to Option 14, wherein:

[0046] The first race of the bearing includes: a radial side that is away from the central axis; and an axial side that is disposed transversely to the radial side, such that the radial side and the axial side are adjacent to each other;

[0047] The housing includes a shoulder that extends along the radial side of the bearing and along the axial side of the bearing; and

[0048] When a high load is applied axially to the bearing, the axial ring engages the shoulder.

[0049] Solution 16. The noise, vibration, and acoustic roughness reduction component according to Solution 14, wherein:

[0050] The first race of the bearing includes: a radial side that is away from the central axis; and an axial side that is disposed transversely to the radial side, such that the radial side and the axial side are adjacent to each other;

[0051] The housing includes a shoulder that extends along the radial side of the bearing and along the axial side of the bearing;

[0052] The housing includes an axial wall facing the axial side of the bearing;

[0053] The axial body of the axial ring includes a plurality of axial corrugations; and

[0054] When a low load is applied axially to the bearing, the axial corrugations engage the axial side of the bearing and the axial wall of the housing to stabilize the bearing.

[0055] Option 17. Noise, vibration, and acoustic roughness reduction component according to Option 14:

[0056] The bearing's first race includes: a radial side facing away from the central axis; a first axial side disposed transversely to the radial side; and a second axial side opposite to the first axial side and disposed transversely to the radial side.

[0057] The housing includes an axial wall facing the first axial side of the bearing;

[0058] The axial ring is further defined as a first axial ring, which is axially disposed relative to the central axis between the first axial side of the first seat ring and the axial wall of the housing; and

[0059] It further includes a second axial ring, which is axially disposed relative to the central axis along the second axial side of the first seat ring.

[0060] Option 18. The noise, vibration, and acoustic roughness reduction assembly according to Option 1, further comprising a snap ring that engages the axial ring and the housing to retain the axial ring relative to the component.

[0061] Option 19. An axial ring disposed along the axial direction of a component, the axial ring comprising:

[0062] An axial body that extends outward to a first axial distal edge and a second axial distal edge that are opposite each other;

[0063] An axial flange that protrudes away from one of the first axial distal edge and the second axial distal edge;

[0064] Multiple axial corrugations are disposed on the axial body and between the first axial distal edge and the second axial distal edge; and

[0065] The axial body is configured to attenuate axial sound-induced vibrations in response to the operation of the component.

[0066] Option 20. A method for attenuating axial and radial sound-induced vibrations in response to the operation of components within a housing, wherein the axial ring is disposed transversely to the radial ring along the component, the method comprising:

[0067] Select the torque applied to the radial ring;

[0068] The stiffness of the radial ring is determined based on a stiffness-torque curve, which utilizes a selected torque to attenuate radial noise in response to the operation of the component.

[0069] The stiffness of the axial ring is determined based on the axial load and the selected torque of the radial ring.

[0070] Manufacture the radial ring to satisfy the determined stiffness of the radial ring;

[0071] Manufacture the axial ring to satisfy the determined stiffness of the axial ring;

[0072] The contour of the component is manufactured within a torque range higher than the selected torque applied to the radial ring; and

[0073] The axial ring is arranged along the axial direction of the component to attenuate axial sound in response to the operation of the component.

[0074] The detailed description and accompanying drawings support and describe this disclosure, but the scope of the claims is defined solely by the claims. While some of the best modes and other configurations for carrying out the claims have been described in detail, various alternative designs and configurations exist for practicing the disclosure as defined in the appended claims. Attached Figure Description

[0075] Figure 1 This is a schematic illustration of a movable platform used as an example to implement a noise, vibration, acoustic roughness reduction component.

[0076] Figure 2 This is a schematic cross-sectional view of a transmission as an example, which utilizes a noise, vibration, and acoustic roughness reduction component.

[0077] Figure 3 This is a schematic plan view of the axial ring.

[0078] Figure 4 This is a schematic plan view of another axial ring.

[0079] Figure 5 This is a schematic partial cross-sectional view of a noise, vibration, acoustic roughness reduction component.

[0080] Figure 6 This is a schematic partial cross-sectional view of a noise, vibration, acoustic roughness reduction component with a single radial ring and a single axial ring.

[0081] Figure 7 This is a schematic partial cross-sectional view of a noise, vibration, acoustic roughness reduction component with a single radial ring and two axial rings.

[0082] Figure 8 This is a schematic partial perspective side view of the shell that defines the recesses and paths.

[0083] Figure 9 This is a schematic partial cross-sectional view relative to the radial and axial rings of the bearing.

[0084] Figure 10 This is a schematic partial cross-sectional view of the radial and axial rings disposed between the housing and the bearing.

[0085] Figure 11 This is a schematic diagram of a controller that includes data on the torque-stiffness curve.

[0086] Figure 12 This is a schematic diagram of a high-load region relative to the radial ring.

[0087] Figure 13 This is a schematic diagram of two high-load regions relative to the radial ring.

[0088] Figure 14 This is a flowchart of a method for reducing component roughness by utilizing noise vibration. Detailed Implementation

[0089] Those skilled in the art will recognize that all directional references (e.g., above, below, up, facing upward, down, facing downward, top, bottom, left, right, vertical, horizontal, etc.) are used to describe the figures to aid the reader’s understanding and do not imply any limitation on the scope of this disclosure as defined by the appended claims (e.g., position, orientation, or use, etc.).

[0090] Referring to the accompanying drawings, where similar figures throughout several views indicate similar or corresponding parts, the noise, vibration, acoustic roughness (or sound) reduction component 10 is typically in... Figure 1 The example embodiment of the noise vibration and acoustic roughness reduction component 10 is shown. Generally, the noise vibration and acoustic roughness reduction component 10 can be used to attenuate sound generated or produced via moving parts, which will be discussed further below. That is, for example, the noise vibration and acoustic roughness reduction component 10 can be used to attenuate sound-induced vibrations generated or produced via moving parts.

[0091] Specifically, such as Figure 1 As shown, the noise, vibration, and roughness reduction component 10 can be used in a mobile platform 12. Non-limiting examples of the mobile platform 12 may include vehicles, automobiles, trucks, motorcycles, off-road vehicles, agricultural vehicles, boats, aircraft, rail vehicles, or other suitable mobile platforms 12. Additionally, the vehicle may be a diesel / gas-powered vehicle, a hybrid vehicle, an electric vehicle, etc. It will be understood that, alternatively, the noise, vibration, and roughness reduction component 10 can be used in non-vehicle applications such as agricultural equipment, fixed platforms, fixed or mobile power plants, robots, conveyors, transport platforms, hard disk drives, air conditioning units, etc. For illustrative purposes, the following description will be in the context of a vehicle. Figure 1 The teachings are intended for mobile platforms 12, rather than being limited to vehicle applications in general.

[0092] continue Figure 1 The vehicle may include a prime mover 14 and a transmission 16 coupled to the prime mover 14. Typically, the prime mover 14 generates power to propel the vehicle, and the transmission 16 provides directional control of the vehicle (such as driving, reversing, and parking) and may also provide speed and torque conversion of the power from the prime mover 14. The prime mover 14 may have a suitable configuration to generate power to propel the vehicle. For example, non-limiting examples of the prime mover 14 may include one or more of the following: an engine, an internal combustion engine, an electric motor, an electric traction motor, etc.

[0093] Typically, transmission 16 is coupled to prime mover 14 to receive intermediate torque 25 output from prime mover 14. Transmission 16 and prime mover 14 may each include a housing 18, wherein the respective housings of transmission 16 and prime mover 14 are rigidly attached to each other. Prime mover 14 may include an output shaft 20, and transmission 16 may include an input member 22. The output shaft 20 of prime mover 14 rotates at engine speed (see arrow 24), and the intermediate torque 25 generated by the rotation of output shaft 20 is transferred to input member 22 of transmission 16, causing input member 22 to rotate. Non-limiting examples of transmission 16 may include automatic transmissions, dual-clutch transmissions, automatic-manual transmissions, continuously variable transmissions (CVTs), etc.

[0094] continue Figure 1The transmission 16 may include: a final drive member 26 coupled to the input member 22; and an output member 28 that delivers output torque (see arrow 30) via the final drive member 26 to one or more drive axles 32 and ultimately to a set of wheels 34. Thus, intermediate torque 25 from the prime mover 14 is transferred to the transmission 16, and the transmission presents output torque 30 to drive the wheels 34. It will be understood that the final drive member 26 may be driven by a ring-shaped rotatable member, and non-limiting examples of the ring-shaped rotatable member may include a belt or chain.

[0095] Alternatively, the vehicle may include a torque converter 36 operable between the output shaft 20 and the input member 22 (see [link to torque converter]). Figure 1 For example, torque converter 36 can be connected to the output shaft 20 of prime mover 14 and the input member 22 of transmission 16. Thus, the output shaft 20 of prime mover 14 can be rotated to transfer intermediate torque 25 in one direction to the input member 22 of transmission 16 via torque converter 36. Therefore, torque converter 36 can provide a desired multiplication of intermediate torque 25 from prime mover 14 to transmission 16 at low speeds.

[0096] Typically, the noise and vibration roughness reduction component 10 can be used to attenuate sound generated or produced by moving parts such as the prime mover 14, transmission 16, differential, etc. That is, for example, the noise and vibration roughness reduction component 10 can be used to attenuate sound-induced vibrations generated or produced by moving parts such as the prime mover 14, transmission 16, differential, etc. Moving parts may generate noise during operation, and this noise can radiate outwards to other parts; this can be referred to as structurally propagated noise. For example, this noise can radiate to the outside of the prime mover 14, transmission 16, differential, etc., and can then be heard by the occupants of the vehicle; therefore, it is desirable to attenuate this noise. Therefore, the noise and vibration roughness reduction component 10 is designed to attenuate sounds, such as noise, generated during the operation of moving parts.

[0097] The noise and vibration roughness reduction assembly 10 can use impedance mismatch to reduce the sound audible due to sound generated or produced via a moving part. For example, the moving part may vibrate at one or more frequencies to produce sound radiating outward to other locations. Impedance mismatch is in which the noise and vibration roughness reduction assembly 10 counteracts the one or more frequencies generated via the moving part, which reduces the sound audible outside the housing 18 of the moving part. Impedance mismatch allows the vibration of the moving part to pass through a radial ring 44 of the noise and vibration roughness reduction assembly 10. The radial ring 44 reduces the force and amplitude of the sound transmitted to the housing 18 (compared to the sound transmitted to the housing 18 without the radial ring 44). This sound reduction is achieved through a higher level of structural compliance than either the vibration of the housing 18 or the vibration of the moving part. This impedance mismatch provides a degree of isolation between the moving part and the housing 18. Additional details of the radial ring 44 can be found in U.S. Application No. 17 / 141,594, filed January 5, 2021, which is incorporated herein by reference in its entirety.

[0098] refer to Figure 2 and Figure 9 The noise, vibration, and roughness reduction component 10 includes a housing 18 and a component 38 supported via the housing 18. The housing 18 may contain various moving parts, some of which may be component 38. For example, the housing 18 may contain moving parts (including component 38) of a prime mover 14, a transmission 16, a differential, etc. Therefore, the housing 18 may be a transmission housing, an engine housing, an electric motor housing, a differential housing, etc. In some configurations, such as... Figure 1 As best shown, housing 18 may define a hole 40 along central axis 42. Depending on the location of hole 40 and type of housing 18, output shaft 20, input member 22, or output member 28, etc., may be disposed through hole 40.

[0099] Component 38 is movable relative to housing 18. In some configurations, component 38 is rotatable about central axis 42. Furthermore, in some configurations, component 38 is rotatable about central axis 42, which creates a high-load area on the taller component 38 (see...). Figure 12 and Figure 13 For example, torque Ts can be generated via rotation of component 38 (see...). Figure 11The torque Ts creates high-load areas that generate vibrations, ultimately producing a sound that the ring is designed to counteract. That is, the operation of component 38 generates or produces vibrations that produce sounds (such as noise) that can be heard outside the housing 18. It is desirable to attenuate this sound. Component 38 can be of various configurations, and non-limiting examples of component 38 may include one or more bearings 46, multiple shafts 47 including output shaft 20, multiple gears 48, multiple components including input member 22 and output member 28, etc. It will be understood that component 38 may include one or more moving parts.

[0100] like Figure 5 As best shown, the axial ring 144 may be positioned adjacent to or between certain parts to attenuate sound in response to the operation of the moving parts and thus reduce noise audible outside the housing 18. Therefore, the noise vibration and acoustic roughness reduction assembly 10 includes an axial ring 144 disposed axially along the component 38. Typically, the axial ring 144 is configured to attenuate axial sound-induced vibrations in response to the operation of the component 38. Thus, movement of the component 38 can generate or produce vibrations that produce one or more frequencies that radiate through the housing 18, and the axial ring 144 is designed to counteract one or more of these frequencies to attenuate sound radiated outside the housing 18. Therefore, the axial ring 144 can be used to generate impedance mismatch.

[0101] like Figure 3 and Figure 4 As best shown, the axial ring 144 can be continuous. That is, the axial ring 144 continuously surrounds the central axis 42. In other words, the axial ring 144 completely surrounds the central axis 42. Thus, the axial ring 144 is continuous to form an inner aperture 165 completely surrounded by the axial ring 144. Typically, the axial ring 144 prevents sound from being transmitted axially out of the axial ring 144. Therefore, sound axially radiated due to the movement of the component 38, caused by the axial ring 144 being axially connected to the component 38, will be attenuated via the axial ring 144. By forming the axial ring 144 as continuous, without spaces, gaps, etc., sound is allowed to leave the axial ring 144 axially.

[0102] The axial ring 144 can be positioned relative to component 38 in various locations. In some configurations, the axial ring 144 is axially disposed between component 38 and housing 18 relative to the central axis 42. For example, the axial ring 144 is guided to housing 18 to secure it to housing 18. In other configurations, the axial ring 144 is axially disposed along component 38. For example, the axial ring 144 is guided to component 38 to secure it to component 38.

[0103] The axial ring 144 includes an axial body 152 extending outwardly to a first axial distal edge 154 and a second axial distal edge 156 opposite to each other. The first axial distal edge 154 is radially spaced from the second axial distal edge 156 relative to the central axis 42. The first axial distal edge 154 faces inwardly toward the central axis 42, and the second axial distal edge 156 faces outwardly away from the central axis 42.

[0104] In various embodiments, the axial body 152 may be continuous. That is, the axial body 152 may be continuous such that the axial body 152 completely surrounds the central axis 42. Thus, the axial body 152 of the axial ring 144 is continuous to form an inner aperture completely surrounded by the axial body 152. Typically, the axial body 152 prevents sound from being transmitted axially out of the axial ring 144. That is, the axial body 152 is configured to attenuate axial sound-induced vibrations in response to the operation of the component 38. Therefore, sound axially radiated due to the movement of the component 38 will be attenuated via the axial body 152 due to the axial alignment of the axial ring 144 with the component 38. By forming the axial body 152 as continuous, without spaces, gaps, etc., sound is allowed to leave the axial ring 144 axially. In some embodiments, the axial body 152 may be continuous. That is, the axial body 152 may include a portion and / or a complete radial gap around the central axis 42.

[0105] Optionally, the axial ring 144 may include other features for guiding the axial ring 144. For example, the axial ring 144 may include an axial flange 150 that protrudes away from one of the first axial distal edge 154 and / or the second axial distal edge 156. In some configurations, the axial flange 150 is guided to the housing 18 to secure the axial ring 144 to the housing 18. In other configurations, the axial flange 150 is guided to the component 38 to secure the axial ring 144 to the component 38.

[0106] In some configurations, more than one axial flange 150 may be used. Therefore, optionally, the axial flange 150 may further include a plurality of axial flanges 150A-150B and 150C-150D spaced apart from each other. In some configurations, each of the axial flanges 150C-150D may extend inwardly toward the central axis 42 from a first axial distal edge 154. In other configurations, each of the axial flanges 150A-150B may extend away from the axial body 152 from a second axial distal edge 156. In some embodiments (see...) Figure 4 and Figure 5 Axial flanges 150A-150B may extend outward away from the central axis 42 in the same plane as the axial body 152. In other embodiments (see...) Figure 7 and Figure 10Axial flanges 150A-150D may extend at right angles away from the plane of axial body 152 and connect to bearing 46 or housing 18.

[0107] In various configurations, the axial body 152 of the axial ring 144 may include a plurality of axial corrugations 164. For example, the axial corrugations 164 of the axial body 152 may be disposed between a first axial distal edge 154 and a second axial distal edge 156. The axial corrugations 164 project outward and / or inward relative to the axial body 152. Furthermore, the axial corrugations 164 are closed. That is, the axial corrugations 164 are characterized by the absence of holes, openings, etc., to prevent sound from escaping through the axial ring 144 via such holes, openings, etc. The axial corrugations 164 may have suitable configurations, and non-limiting examples may include circular, square, elliptical, rectangular, overall, cross-shaped, elongated, etc., and combinations thereof. Furthermore, the axial corrugations 164 may have suitable patterns or positions along the axial body 152.

[0108] Furthermore, the axial corrugations 164 may overlap with a portion of component 38. For example... Figure 3 , Figure 4 and Figure 6 As best shown, the first side 168A of the axial corrugation 164 may be adjacent to the housing 18 or component 38, and the second side 168B of the axial corrugation 164 may be spaced apart from another in the housing 18 or component 38. For example, in such Figure 6 In one configuration shown, a first side 168A of the axial corrugation 164 abuts against member 38, and a second side 168B of the axial corrugation 164 is spaced apart from housing 18 to present an axial pocket 170. Furthermore, when one or more forces are applied to the axial body 152 in response to operation of member 38, the axial corrugation 164 allows the axial body 152 to be elastically compressed. The axial corrugations 164 are constructed in a desired configuration and spaced apart from each other at a desired distance to present an axial body 152 with desired stiffness characteristics, which are further discussed below. The axial corrugations 164 along the axial body 152 also function to control the position of the axial ring 144 relative to housing 18 with acceptable positional tolerances.

[0109] In some configurations, as mentioned above, component 38 may include a bearing 46 disposed in bore 40. For example, bearing 46 may be used to reduce friction between a rotating shaft 47 (which may include output shaft 20, input member 22, or output member 28, etc.) and a stationary component 38 (such as housing 18). Furthermore, bearing 46 may support the rotating shaft 47. Axial ring 144 may be axially disposed relative to central axis 42 along bearing 46. Therefore, due to the axially positioned axially along bearing 46, axial ring 144 attenuates sound propagating axially outward from bearing 46 toward housing 18.

[0110] As in Figure 8 and Figure 10 As shown in the optimal configuration, the housing 18 may define a recess 82 connected to the hole 40, such that the recess 82 is open to the hole 40 (see [reference]). Figure 2 And facing the central axis 42. The radial body 52 of the radial ring 44 may be disposed in the recess 82, and the radial side 78A of the component 38 faces the recess 82. Thus, the housing 18 may present a rear wall 84, a first shoulder 86 and a second shoulder 88 spaced apart from each other to surround the recess 82 along three sides (see Figure 6 The first radially distal edge of the radial body 52 may face the first shoulder 86, and the second radially distal edge of the radial body 52 may face the second shoulder 88.

[0111] Furthermore, the housing 18 may define a path 90 for connection to the recess 82 (see Figure 8 The radial flange 50 is disposed in the path 90 to fix the position of the radial body 52 of the radial ring 44 relative to the housing 18 and the bearing 46 (e.g., in some configurations, the first race 92 of the bearing 46). More specifically, the path 90 may be defined through a first shoulder 86 of the housing 18. In some configurations, the path 90 may extend axially relative to the central axis 42, and the radial flange 50 may extend axially into the path 90 relative to one of the first and second radially distal edges. In other configurations, the path 90 may extend radially relative to the central axis 42, and the radial flange 50 may extend laterally into the path 90 relative to one of the first and second radially distal edges. In yet another configuration, the path 90 may extend both axially and radially relative to the central axis 42 (see...). Figure 10 The radial flange 50 extends both axially and radially from one of the first and second radially distal edges into the path 90. The housing 18 may be constructed with a suitable number of paths 90 as discussed above, depending on the number of radial flanges 50 used (e.g., 50A to 50C). It will be understood that if the plurality of radial flanges 50 are used, the housing 18 may define a plurality of paths 90, and each of these paths 90 may have the configuration discussed above for the path 90.

[0112] In some configurations, as mentioned above, component 38 may include a bearing 46 disposed in bore 40 (see Figure 2 and Figure 9More specifically, the radial side 78A of the bearing 46 may face the recess 82. For example, the bearing 46 may be used to reduce friction between a rotating shaft 47 (which may include an output shaft 20, an input member 22, or an output member 28, etc.) and a stationary component 38 (such as a housing 18). Furthermore, the bearing 46 may support the rotating shaft 47. A radial ring 44 is radially disposed between the bearing 46 and the housing 18 relative to the central axis 42. Therefore, due to the radially positioned radial ring 44 between the bearing 46 and the housing 18, the radial ring 44 attenuates sound propagating radially outward from the bearing 46 toward the housing 18.

[0113] continue Figure 10 The bearing may include: a first race 92 fixed to the housing 18; and a second race 94 rotatable relative to the first race 92 about a central axis 42. One or more ball bearings 93 are disposed between the first race 92 and the second race 94. The second race 94 may be disposed relative to the central axis 42 closer to the central axis 42 than the first race 92. Typically, the radial body 52 of the radial ring 44 may be disposed adjacent to the first race 92. For example, the radial body 52 may be disposed axially relative to the central axis 42 along the first race 92. Thus, the radial body 52 of the radial ring 44 may be adjacent to the first race 92. When a radial flange 50 is used, the radial flange 50 bends around the first race 92, or the radial flange 50 extends axially from the radial body 52 (i.e., does not bend transversely to the radial body 52).

[0114] The radial body 52 includes a length L between the first axial distal edge 154 and the second axial distal edge 156. The length L of the radial body 52 axially overlaps with the first race 92. That is, the radial body 52 extends radially outward relative to the central axis 42 to overlap a portion of the component 38. Therefore, the radial body 52 extends this length radially relative to the central axis 42 to axially overlap with the first race 92. It will be understood that the length L of the radial body 52 may be longer or shorter than the length shown in the figure. It will also be understood that the length L of the radial body 52 does not extend beyond the first race 92 relative to the second race 94. That is, the length L of the radial body 52 does not extend to the rotating portion of the bearing 46, i.e., does not extend to the second race 94. The bearing 46 may be a ball bearing, a cylindrical bearing, a roller bearing, or other suitable bearing using races.

[0115] refer to Figure 10The first race 92 of the bearing 46 may include: a radial side 78A, which is opposite to the central axis 42; and an axial side 78B, which is disposed transversely to the radial side 78A, such that the radial side 78A and the axial side 78B are adjacent to each other. Furthermore, the housing 18 may include an axial shoulder 122 extending along the radial side 78A and along the axial side 78B of the bearing 46. Additionally, the housing 18 may include an axial wall 120 facing the axial side 78B of the bearing 46.

[0116] In some configurations, when a high (or first) load 116 is applied axially to bearing 46, the axial ring 144 engages the axial shoulder 122. The high load 116 can be a force greater than several thousand (e.g., >5,000) Newtons. In other configurations, when a low (or second) load 118 is applied axially to bearing 46, the axial corrugation 164 engages the axial side 78B of bearing 46 and the axial wall 120 of housing 18 to stabilize bearing 46. The low load 118 can be a force less than several thousand (e.g., <5,000) Newtons. Other thresholds for the high load 116 and low load 118 may be implemented to meet the criteria for a particular application.

[0117] Optionally, the axial ring 144 can be used in more than one location. The axial side 78B of the first race 92 may be referred to as the first axial side 124. The first race 92 of the bearing 46 may include a radial side 78A as discussed above. The first axial side 124 is disposed transversely to the radial side 78A, and the second axial side 126 is opposite to the first axial side 124 and disposed transversely to the radial side 78A. Thus, in this configuration, the axial wall 120 of the housing 18 faces the first axial side 124 of the bearing 46. In one configuration, the axial ring 144 abuts the first axial side 124 of the first race 92. In another configuration, the axial ring 144 abuts the second axial side 126 of the first race 92.

[0118] In another configuration, more than one axial ring 144 may be used. Thus, optionally, the axial ring 144 is further defined as a first axial ring 144A and further includes a second axial ring 144B axially spaced from the first axial ring 144A. Therefore, in this configuration, the bearing 46 may be disposed between the first axial ring 144A and the second axial ring 144B. For example, the first axial ring 144A may be axially disposed relative to the central axis 42 between the first axial side 124 of the first race 92 and the axial wall 120 of the housing 18, and the second axial ring 144B may be axially disposed relative to the central axis 42 along the second axial side 126 of the first race 92.

[0119] Alternatively, the buckle 110 (see also...) Figure 5 , Figure 7 and Figure 10A snap ring 110 can be used to secure the axial ring 144 to the bearing 46 or the housing 18. For example, a snap ring 110 can engage the axial ring 144 and the housing 18 to retain the axial ring 144 relative to the component 38. More specifically, the snap ring 110 can engage the axial ring 144 (e.g., 144A) and the axial wall 120 of the housing 18. When the axial ring 144 is positioned along the second axial side 126 of the bearing 46, the snap ring 110 can engage the axial ring 144 (e.g., 144A) and the axial wall 120 of the housing 18. Figure 7 and Figure 10 The axial ring 144 is located in recesses in the second axial side 126 of the housing 18 and / or bearing 46 to retain the axial ring 144 relative to the component 38. In various embodiments, the snap ring 110 and the axial ring 144 may be integrated into a single component. It will be understood that if more than one axial ring 144 is used, more than one snap ring 110 may be used.

[0120] As discussed above, component 38 may include shaft 47, and bearing 46 supports rotation of shaft 47. Therefore, for example, rotation of shaft 47 (which may include output shaft 20, input member 22, or output member 28, etc.) creates high-load regions HL, HL1, HL2 on bearing 46. That is, the torque Ts generated due to the rotation of shaft 47 creates high-load regions HL, HL1, HL2, which are transferred to bearing 46. The first shoulder 86 and the second shoulder 88 of housing 18 support higher torques, such as torque Ts, generated via rotation of shaft 47. (Reference) Figure 12 In some configurations, a high-load region HL is created on bearing 46. The body 52 of radial ring 44 is positioned along the high-load regions HL, HL1, HL2 to maximize the attenuation of sound in response to the operation of shaft 47. Therefore, the opening 62 of radial ring 44 is spaced apart from the high-load regions HL, HL1, HL2. That is, the opening 62 of radial ring 44 does not attenuate sound, so it is desirable to position the opening 62 away from the high-load regions HL, HL1, HL2 that generate or produce the sound to be attenuated. Typically, the high-load regions HL, HL1, HL2 can generate a force F equal to or greater than 5 kilonewtons (kN). More specifically, as a non-limiting example, the force F generated in the high-load regions HL, HL1, HL2 can be from about 5 kN to about 30 kN.

[0121] The radial ring 44 can be tuned to a desired frequency to attenuate the sound generated along the high-load regions HL, HL1, HL2. For example, the radial ring 44 can be formed with a stiffness Ks (see...). Figure 11The radial ring 44 is designed to attenuate sound along the high-load regions HL, HL1, and HL2. Typically, the stiffness Ks of the radial ring 44 is the degree to which the body 52 of the radial ring 44 resists deformation in response to forces F applied from the high-load regions HL, HL1, and HL2. Therefore, the more rigid the body 52 of the radial ring 44, the less deformation it will undergo in response to forces, and vice versa. Consequently, the body 52 will vibrate at different rates depending on the stiffness Ks, and thus the frequency of the radial ring 44 can be tuned to a desired frequency to attenuate sound generated during the operation of component 38. Therefore, the frequency of the radial ring 44 cancels out the frequency of component 38 to attenuate sound radiated outward from housing 18. Generally, radially and axially reducing the stiffness Ks helps reduce sound audible outside housing 18.

[0122] Optionally, the radial ring 44 can be designed to attenuate multiple frequencies of sound. Therefore, the radial ring 44 can have different regions with different stiffness K. s1 K s2 For example, the body 52 of the radial ring 44 may include: a first portion 98 that provides a first ring stiffness K. s1 ; and the second part 100, which provides the same stiffness K as the first ring. s1 Different second ring stiffness K s2 For example, refer to Figure 13 The rotation of shaft 47 generates a first high-load region HL1 on bearing 46 under a first condition, and a second high-load region HL2 on bearing 46 under a second condition. The first high-load region HL1 and the second high-load region HL2 are different. Body 52 has a first ring stiffness K. s1 The first part 98 is aligned with the first high-load region HL1 to maximize the attenuation of sound in the first high-load region HL1, and the body 52 has a second ring stiffness K. s2 The second part 100 is aligned with the second high-load region HL2 to maximize the attenuation of sound in the second high-load region HL2. It will be understood that the radial ring 44 can be designed with a suitable number of rings with different stiffness K. s1 K s2 Parts 98 and 100. It will also be understood that radial ring 44 may have parts 98 and 100 with different stiffness.

[0123] For example, refer to Figure 13 If a radial ring 44 is used in the transmission 16, then due to the operation of the transmission 16 under the first and second conditions, the first resultant force F in the first direction will be... r1 With the second resultant force F along the second direction r2 Different. The first resultant force F along the first direction r1This generates the first high-load region HL1, which, along with the second resultant force F in the second direction, creates a second high-load region HL1. r2 The conditions differ. The first condition could be when the transmission 16 operates in drive mode, in which the movable platform 12 is propelled, and the second condition could be when the transmission 16 operates in regenerative braking mode, in which energy is recovered during braking of the movable platform 12, and this energy can be used immediately or stored in an energy storage device for later use. Changes in load direction allow for new stiffness on the corresponding reaction arc, and therefore, the radial ring 44 can be designed with different stiffnesses K. s1 K s2 Changing the direction of the output torque (e.g., driving to coasting or regenerative braking) alters the load direction, allowing for new stiffness on the corresponding reaction arc. Furthermore, if multiple prime movers 14 interact with the output shaft 20 (e.g., in hybrid vehicles, where torque from the engine on one gear and torque from the electric motor are also transmitted through the same output shaft 20 by different gears, which may be at different unrelated torque levels), the radial ring 44 can be designed with different stiffnesses K. s1 K s2 .

[0124] This disclosure also provides a method for attenuating sound using a radial ring 44 in response to the operation of a component 38 within the housing 18. Parameters of the radial ring 44 are determined, and then those parameters are used to form the radial ring 44. For example, a torque Ts applied to the radial ring 44 is selected. The torque Ts is a given value based on the torque applied to the component 38. For example, the torque Ts generated by the rotation of the shaft 47 is applied as a force F to the bearing 46 and ultimately as a force F to the radial ring 44.

[0125] Based on the torque-stiffness curve TK (see...) Figure 11 The torque-stiffness curve of the radial ring 44 is determined by using a selected torque Ts to maximize the attenuation of sound in response to the operation of component 38. That is, the radial ring 44 needs to be designed with a desired stiffness Ks in order to attenuate sound. Figure 11 The graph illustrates the torque-stiffness curve TK, where the y-axis provides the value of stiffness K and the x-axis provides the value of torque T. Therefore, the stiffness Ks of the radial ring 44 can be found by identifying the value of torque Ts on the torque-stiffness curve TK. The value of stiffness Ks is found at the intersection of the torque-stiffness curves TK. Continuing... Figure 11 The chart shows that the first range X1 of the torque T of the radial ring 44 is at or below the selected torque Ts. Based on these values, the radial ring 44 is manufactured to meet a determined stiffness Ks.

[0126] The torque-stiffness curve TK was developed via system analysis to meet the misalignment and deflection requirements of the radial ring 44. The permissible misalignment limits are met because the gear teeth deflect under load and clearance affect the contact. The radial ring 44 can be designed using the finite element method (FEM), which subdivides a large system into smaller, simpler pieces as finite elements. For example, one or more simple equations are used to model the finite element model, and these equations are then combined into a larger set of equations to ultimately model the torque-stiffness curve TK; this can be referred to as finite element analysis (FEA).

[0127] The transmission 16 may include various gears 48 coupled to the shaft 47, and therefore, as discussed above, component 38 may include gears 48. Gears 48 can be used to change the operating mode of the transmission 16 or the torque output to the wheels 34 by changing the gear ratio of certain gears 48. The outline 102 of gear 48 (see...) Figure 9 It can also be used to tune the radial ring 44 to the desired stiffness Ks. The profile 102 of component 38 (here, one or more gears 48) is in the second range X2 of torque T (see... Figure 11 Manufactured at the location shown in the diagram), this torque is higher than the selected torque Ts applied to the radial ring 44; therefore, the profile 102 of the (multiple) gears 48 is designed to have a torque Ts higher than that of the radial ring 44 and not greater than the maximum torque Tmax (i.e., in the second range X2 (see diagram)). Figure 11 The torque T is within the diagram. For example, to optimize the profile 102 of (multiple) gears 48, system modeling and noise-vibration-harshness (NVH) modeling can be used. System modeling treats gear 48 as a source and the response of housing 18. NVH modeling can be used to study and modify the acoustic characteristics, such as noise and vibration characteristics, of component 38 during operation (e.g., movement or rotation of component 38). For example, when component 38 is gear 48, system modeling and NVH modeling can be used to optimize the profile 102 of gear 48 for torque T while bearing 46 is supported via housing 18.

[0128] Therefore, controller 104 (see Figure 11The controller 104 performs FEM, which includes FEA, system modeling, and NVH modeling. Instructions may be stored in memory 106 of the controller 104 and executed automatically via processor 108 of the controller 104 to provide corresponding control and modeling functions. The controller 104 is configured to execute instructions from memory 106 via processor 108. For example, the controller 104 may be a host or distributed system (e.g., a computer such as a digital computer or microcomputer) and the memory 106 may be a tangible, non-transitory computer-readable memory (such as read-only memory (ROM) or flash memory). The controller 104 may also have random access memory (RAM), electrically erasable programmable read-only memory (EEPROM), a high-speed clock, analog-to-digital (A / D) and / or digital-to-analog (D / A) circuitry, and appropriate input / output circuitry and associated means, as well as appropriate signal conditioning and / or signal buffering circuitry. Therefore, controller 104 may include all the software, hardware, memory 106, algorithms, connections, sensors, etc., necessary for controlling, designing, and / or modeling, for example, the data used for radial loop 44 and component 38. Thus, the control methods used to design radial loop 44 and component 38 may be embodied in software or firmware associated with controller 104. Optionally, more than one controller 104 may be used.

[0129] The radial ring 44 may be manufactured with one or more of the features discussed above (such as corrugations), and these will not be repeated. After the radial ring 44 is manufactured with the desired stiffness Ks and the orientation of the flanges 50A, 50B, 50C, the radial ring 44 is radially disposed between the component 38 and the housing 18 to attenuate sound in response to the operation of the component 38. For example, in some configurations, the body 52 may be disposed in the recess 82 of the housing 18 before the bearing 46 is placed relative to the housing 18. Due to the discontinuous configuration of the body 52, the radial ring 44 may be compressed or squeezed, which causes the outer diameter of the radial ring 44 to shrink and allows the radial ring 44 to be inserted into the hole 40 of the housing 18 and aligned with the recess 82. The flanges 50A, 50B, 50C of the radial ring 44 are disposed in the path 90 of the housing 18, and once the body 52 is aligned with the recess 82, the radial ring 44 is released to house the body 52 within the recess 82 and at least partially decompress the radial ring 44. After the radial ring 44 is positioned in the recess 82 of the housing 18, the component 38 (such as the bearing 46) can be press-fitted into the housing 18 within the bore 40 of the housing 18 until the desired compressive load is applied to the radial ring 44.

[0130] refer to Figure 14A flowchart of an example method 180 for using a noise vibration acoustic roughness reduction component 10 is shown. Method 180 utilizes an axial ring 144 and a radial ring 44 to attenuate axial and radial acoustically induced vibrations in response to the operation of a component 38 within a housing 18. The axial ring 144 is positioned transversely to the radial ring 44 along the component 38.

[0131] In step 182, specifications for the noise, vibration, and roughness reduction component 10 are provided. In step 184, parameters of the radial ring 44 are determined, and then the radial ring 44 is formed based on those parameters. For example, in step 186, the torque Ts applied to the radial ring 44 is selected. The torque Ts is a given value based on the torque applied to component 38. For example, the torque Ts generated by the rotation of shaft 47 is applied as a force F to bearing 46, and ultimately as a force F to radial ring 44.

[0132] In step 188, the stiffness of the radial ring 44 is determined based on a stiffness-torque curve that utilizes a selected torque to attenuate radial noise in response to the operation of component 38. In step 190, the stiffness of the axial ring 144 is determined based on the axial load and a selected torque for the radial ring 44. In step 192, the radial ring 44 is manufactured to meet the determined stiffness of the radial ring 44. In step 194, the axial ring 144 is manufactured to meet the determined stiffness of the axial ring 144. In step 196, the profile 102 of component 38 is manufactured within a torque range higher than the selected torque applied to the radial ring 44. In step 198, the housing 18 is manufactured.

[0133] In step 200, an axial ring 144 (e.g., a first axial ring 144A) is arranged axially along component 38 to attenuate axial noise in response to operation of component 38. In step 202, a radial ring 44 is radially arranged on component 38. Then, in step 204, a bearing 46 with the radial ring 44 attached is arranged axially along component 38. In step 206, another axial ring 144 (e.g., a second axial ring 144B) is arranged axially along component 38 to further attenuate axial noise in response to operation of component 38. In step 208, a snap ring 110 is arranged axially along component 38 and coupled to housing 18.

[0134] It will be understood that the order or sequence of performing this method is for illustrative purposes, and other orders or sequences are within the scope of this teaching.

[0135] Although the best mode and other configurations for carrying out this disclosure have been described in detail, those skilled in the art will recognize various alternative designs and configurations for practicing this disclosure within the scope of the appended claims. Furthermore, the features of the configurations shown in the drawings or the various configurations mentioned in this description need not be construed as independent of each other. Rather, it is possible that each feature described in one example of a configuration may be combined with one or more other desired features from other configurations, resulting in other configurations that are not described in words or with reference to the drawings. Therefore, such other configurations fall within the scope of the appended claims.

Claims

1. A noise, vibration, and acoustic roughness reduction component, comprising: case; A component that is supported by the housing and is movable relative to the housing; as well as An axial ring, disposed axially along the component, wherein the axial ring is configured to attenuate axial sound-induced vibrations in response to operation of the component. The component is rotatable about a central axis, and the axial ring continuously surrounds the central axis; The axial ring includes an axial body that extends outwardly to a first axial distal edge and a second axial distal edge that are opposite each other; The first axial distal edge is radially spaced from the second axial distal edge relative to the central axis; The first axial distal edge faces inward toward the central axis, and the second axial distal edge faces outward away from the central axis; The axial body of the axial ring includes a plurality of axial corrugations disposed between the first axial distal edge and the second axial distal edge.

2. The noise, vibration, and acoustic roughness reduction component according to claim 1, wherein, The axial ring is axially disposed between the component and the housing relative to the central axis.

3. The noise, vibration, and acoustic roughness reduction component according to claim 2, wherein, The axial ring includes an axial flange that protrudes outward from one of the first axial distal edge and the second axial distal edge.

4. The noise, vibration, and acoustic roughness reduction component according to claim 3, wherein, The axial flange is guided to the housing to secure the axial ring to the housing.

5. The noise, vibration, and acoustic roughness reduction component according to claim 3, wherein, The axial flange is guided to the component to secure the axial ring to the component.

6. The noise, vibration, and acoustic roughness reduction component according to claim 3, wherein, The axial flange further includes a plurality of axial flanges spaced apart from each other, wherein each of the axial flanges extends inward toward the central axis from the first axial distal edge.

7. The noise, vibration, and acoustic roughness reduction component according to claim 3, wherein, The axial flange further includes a plurality of axial flanges spaced apart from each other, wherein each of the axial flanges extends from the second axial distal edge away from the axial body.

8. The noise, vibration, and acoustic roughness reduction component according to claim 1, wherein, The plurality of axial corrugations overlap with a portion of the component.

9. The noise, vibration, and acoustic roughness reduction component according to claim 1, wherein: The housing defines a hole along its central axis; The component includes a bearing disposed in the hole; and The axial ring is arranged axially along the bearing relative to the central axis.

10. The noise, vibration, and acoustic roughness reduction component according to claim 9, wherein: The bearing includes: a first race fixed to the housing; and a second race rotatable about the central axis relative to the first race; and The axial body is axially disposed relative to the central axis along the first seat ring.

11. The noise, vibration, and acoustic roughness reduction component according to claim 10, wherein: The first race of the bearing includes: a radial side that is away from the central axis; and an axial side that is disposed transversely to the radial side, such that the radial side and the axial side are adjacent to each other; The housing includes a shoulder that extends along the radial side of the bearing and along the axial side of the bearing; and When a high load is applied axially to the bearing, the axial ring engages the shoulder.

12. The noise, vibration, and acoustic roughness reduction component according to claim 10, wherein: The first race of the bearing includes: a radial side that is away from the central axis; and an axial side that is disposed transversely to the radial side, such that the radial side and the axial side are adjacent to each other; The housing includes a shoulder that extends along the radial side of the bearing and along the axial side of the bearing; The housing includes an axial wall facing the axial side of the bearing; When a low load is applied axially to the bearing, the axial corrugations engage the axial side of the bearing and the axial wall of the housing to stabilize the bearing.

13. The noise, vibration, and acoustic roughness reduction component according to claim 10: in, The first race of the bearing includes: a radial side that is away from the central axis; a first axial side that is disposed transversely to the radial side; and a second axial side that is opposite to the first axial side and disposed transversely to the radial side. The housing includes an axial wall facing the first axial side of the bearing; The axial ring is further defined as a first axial ring, which is axially disposed relative to the central axis between the first axial side of the first seat ring and the axial wall of the housing; and It further includes a second axial ring, which is axially disposed relative to the central axis along the second axial side of the first seat ring.

14. The noise, vibration, and acoustic roughness reduction assembly of claim 1, further comprising a snap-fit ​​ring that engages the axial ring and the housing to retain the axial ring relative to the component.

15. A method for attenuating axial and radial sound-induced vibrations in response to the operation of components within a housing, wherein, The axial ring is disposed transversely to the radial ring along the component, and the method includes: Select the torque applied to the radial ring; The stiffness of the radial ring is determined based on a stiffness-torque curve, which utilizes a selected torque to attenuate radial noise in response to the operation of the component. The stiffness of the axial ring is determined based on the axial load and the selected torque of the radial ring. Manufacture the radial ring to satisfy the determined stiffness of the radial ring; Manufacture the axial ring to satisfy the determined stiffness of the axial ring; The contour of the component is manufactured within a torque range higher than the selected torque applied to the radial ring; and The axial ring is arranged along the axial direction of the component to attenuate axial sound in response to the operation of the component.

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