WO2024138427A1

WO2024138427A1 - Mounting and fixing mechanism for shaft, and shaft assembly and mounting method therefor

Info

Publication number: WO2024138427A1
Application number: PCT/CN2022/142854
Authority: WO
Inventors: 裘华潮
Original assignee: 舍弗勒技术股份两合公司; 裘华潮
Priority date: 2022-12-28
Filing date: 2022-12-28
Publication date: 2024-07-04

Abstract

A mounting and fixing mechanism for a shaft, the mounting and fixing mechanism comprising: a first ring (1) and a second ring (2), wherein the first ring (1) continuously extends in a circumferential direction of the shaft (6) and forms a notch (lc), the opening diameter of the first ring (1) in a natural state is greater than the outer diameter of the shaft (6), a side face in an axial direction of the first ring (1) is formed as a first inclined surface (11), and the other side face (14) in the axial direction of the first ring (1) is configured to abut against a first mounting member; and the second ring (2) continuously extends on the entire circumference in the circumferential direction of the shaft (6), a side face in an axial direction of the second ring (2) is formed as a second inclined surface (21) that has a shape matching with the first inclined surface (11) and abuts against the first inclined surface (11), and the other side face (24) in the axial direction of the second ring (2) is configured to abut against a second mounting member. In this way, it is possible to prevent axial movement of components and to eliminate noise generated by means of collisions between components in the axial direction. Further provided are a shaft assembly comprising the mounting and fixing mechanism, and a mounting method for the shaft assembly.

Description

Installation and fixing mechanism for shaft, shaft assembly and installation method thereof

Technical Field

The present application relates to a mounting and fixing mechanism, in particular to a mounting and fixing mechanism for a shaft, a shaft assembly including the mounting and fixing mechanism, and a mounting method thereof.

Background technique

A motor as shown in FIG. 1A and FIG. 1B includes a housing 10, a stator 20, a rotor 30, a shaft 40, a bearing 50, a gear 60 and a snap ring 70. Specifically, the stator 20 and the rotor 30 are arranged in the housing 10, the stator 20 is fixed to the housing 10, and the rotor 30 is located at the radial inner side of the stator 20 and can rotate relative to the stator 20. Further, the shaft 40 is fixed to the rotor 30, so that the shaft 40 can rotate with the rotor 30. The bearing 50 is sleeved on the shaft 40 and is located between the housing 10 and the shaft 40, so that the housing 10 can support the shaft 40 via the bearing 50. Further, the gear 60 is sleeved on the shaft 40 in a torsion-proof manner, so that the gear 60 can rotate with the shaft 40. In addition, the outer peripheral surface of the shaft 40 is formed with a shaft shoulder 40s, and the bearing 50 is located between the gear 60 and the shaft shoulder 40s in the axial direction. The outer peripheral surface of the shaft 40 is also formed with an annular groove 40c, and the snap ring 70 is installed in the annular groove 40c. The gear 60 is axially located between the bearing 50 and the snap ring 70. The axial positions of the bearing 50 and the gear 60 are defined by the shaft shoulder 40s and the snap ring 70. Thus, when the gear 60 is a helical gear and is used to transmit torque, the gear 60 will generate an axial force, and the gear 60 can move in the axial direction until the gear 60 is stopped by the bearing 50 or the snap ring 70.

Since each component has a processing error, such as the width of the bearing 50, the width of the gear 60, and the thickness of the snap ring 70, there may be a first gap G1 between the bearing 50 and the gear 60 after assembly, and there may be a second gap G2 between the gear 60 and the snap ring 70. In this way, when the gear 60 changes the torque transmission direction, the first gap G1 between the bearing 50 and the gear 60 and the second gap G2 between the gear 60 and the snap ring 70 will change, thereby causing an unexpected collision noise.

Summary of the invention

This application is made based on the defects of the above-mentioned prior art. One object of this application is to provide a mounting and fixing mechanism for a shaft, which can reduce or even eliminate the noise generated by the undesirable collision described in the background technology. Another object of this application is to provide a shaft assembly including a mounting and fixing mechanism for a shaft and a mounting method thereof.

In order to achieve the above objectives, this application adopts the following technical solutions.

The present application provides a mounting and fixing mechanism for a shaft, which is used to be sleeved between a first mounting member and a second mounting member in the axial direction of the shaft, wherein both the first mounting member and the second mounting member are sleeved on the shaft, and the mounting and fixing mechanism comprises:

A first ring, which continuously extends along the circumference of the shaft and is formed with a notch, the aperture of the first ring in a natural state is larger than the outer diameter of the shaft, one axial side surface of the first ring is formed as a first inclined surface, the first inclined surface extends radially inward and obliquely extends axially toward one side, and the other axial side surface of the first ring is used to abut against the first mounting member; and

The second ring continuously extends along the entire circumference of the shaft, the other axial side surface of the second ring is formed as a second inclined surface that matches and abuts against the first inclined surface, and one axial side surface of the second ring is used to abut against the second mounting piece.

In an optional solution, the angle formed by the first inclined surface and the central axis of the shaft is equal to the angle formed by the second inclined surface and the central axis.

In another optional solution, 90 degrees>α≥75 degrees.

In another optional solution, the side surface of the first ring for abutting against the first mounting member is perpendicular to the central axis of the shaft; and/or

The side surface of the second ring for abutting against the second mounting member is perpendicular to the central axis of the shaft.

In another optional solution, the inner circumference of the first ring and the inner circumference of the second ring are parallel to the central axis of the shaft; and/or

An outer circumferential surface of the first ring and an outer circumferential surface of the second ring are parallel to the central axis of the shaft.

In another optional solution, the angle between the first inclined surface and the central axis of the shaft is α and the friction coefficient between the first inclined surface and the second inclined surface is μ, satisfying μ>tan(90°-α).

The present application also provides a shaft assembly, comprising the installation and fixing mechanism for the shaft as described in any one of the above technical solutions, the shaft, the first installation member and the second installation member.

In an optional solution, the first mounting member is a gear, the second mounting member is a retaining ring, the shaft is formed with an annular groove for mounting the retaining ring, and the width of the annular groove is greater than the width of the retaining ring.

In another optional solution, a bearing is further included, the shaft is formed with a shaft shoulder, and the bearing is located between the shaft shoulder and the gear.

The present application also provides a method for installing a shaft assembly as described in any one of the following technical solutions, comprising:

Sleeve the first mounting member onto the shaft;

Sleeve the first ring onto the shaft, so that the first ring abuts against the first mounting member from one axial side, and compresses the first ring in the radial direction and maintains the compressed state;

Sleeve the second ring onto the shaft so that the second inclined surface of the second ring abuts against the first inclined surface of the first ring;

Fitting the second mounting member onto the shaft; and

The compressed state of the first ring is released to expand the first ring in the radial direction, so that the second ring abuts against the second mounting member from the other axial side.

By adopting the above technical solution, the present application provides a mounting and fixing mechanism for a shaft, which includes a first ring and a second ring assembled with each other. The aperture of the first ring in a natural state is larger than the outer diameter of the shaft and is formed with a notch. The first ring is formed with a first inclined surface, which extends radially inward and obliquely extends axially toward one side, and the other axial side surface of the first ring is used to abut against the first mounting member. The second ring extends continuously along the circumference of the shaft over the entire circumference. The second ring is formed with a second inclined surface, which matches the shape of the first inclined surface and abuts against the first inclined surface, and the axial side surface of the second ring is used to abut against the second mounting member.

Thus, the gaps between the components (including the first mounting member and the second mounting member) mounted on the shaft can be eliminated by the mounting and fixing mechanism, thereby suppressing the axial movement of the components and eliminating the unwanted noise generated by the collision between the axial components, thereby improving the NVH performance of the system (such as the shaft assembly) using the mounting and fixing mechanism. Furthermore, a shaft assembly including the above-mentioned mounting and fixing mechanism and a mounting method thereof are also provided, and the shaft assembly has the same effect.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1A is a partial cross-sectional schematic diagram showing a motor.

FIG. 1B is an enlarged schematic diagram showing a part of the structure in FIG. 1A .

FIG. 2A is a partial cross-sectional schematic diagram showing a shaft assembly according to an embodiment of the present application, wherein the shaft assembly includes a mounting and fixing mechanism for a shaft according to an embodiment of the present application.

FIG. 2B is an enlarged schematic diagram showing a part of the structure in FIG. 2A .

FIG. 3A is a perspective schematic diagram showing a first ring of the shaft assembly in FIG. 2A .

FIG. 3B is a partial cross-sectional schematic diagram showing the first ring in FIG. 3A .

FIG. 3C is a schematic diagram for explaining the size of the first ring in FIG. 3A .

FIG. 4A is a perspective schematic diagram showing a second ring of the shaft assembly in FIG. 2A .

FIG. 4B is a partial cross-sectional schematic diagram showing the second ring in FIG. 4A .

FIG. 4C is a schematic diagram for explaining the size of the second ring in FIG. 4A .

5A , 5B, and 5C are explanatory diagrams for explaining an assembling process of the shaft assembly in FIG. 2A .

Description of Reference Numerals

10 housing; 20 stator; 30 rotor; 40 shaft; 40s shaft shoulder; 40c ring groove; 50 bearing; 60 gear; 70 snap ring; G1 first gap; G2 second gap;

1 first ring; 11 first inclined surface; 12 first inner peripheral surface; 13 first outer peripheral surface; 14 first side surface; 1c notch;

2 second ring; 21 second inclined surface; 22 second inner peripheral surface; 23 second outer peripheral surface; 24 second side surface;

3 gears;

4 snap rings;

5 bearings;

6 shaft; 6s shaft shoulder; 6c ring groove;

A is axial; R is radial.

Detailed ways

The exemplary embodiments of the present application are described below with reference to the accompanying drawings. It should be understood that these specific descriptions are only used to teach those skilled in the art how to implement the present application, and are not intended to exhaust all possible methods of the present application, nor to limit the scope of the present application.

In the present application, unless otherwise specified, "axial", "radial" and "circumferential" refer to the axial, radial and circumferential directions of the shaft, respectively. Further, "one axial side" refers to the right side in Figures 2A, 2B, 3B, 3C, 4B, 4C, 5B and 5C; "the other axial side" refers to the left side in Figures 2A, 2B, 3B, 3C, 4B, 4C, 5B and 5C. Further, "radially outer side" refers to the side radially away from the central axis of the shaft, specifically the upper side in Figures 2A, 2B, 5B and 5C and the lower side in Figures 3B, 3C, 4B and 4C; "radially inner side" refers to the side radially close to the central axis of the shaft, specifically the lower side in Figures 2A, 2B, 5B and 5C and the upper side in Figures 3B, 3C, 4B and 4C.

The structure of the shaft assembly according to an embodiment of the present application will be described below with reference to the accompanying drawings.

As shown in Figures 2A and 2B, the shaft assembly according to an embodiment of the present application includes a mounting and fixing mechanism for the shaft (a first ring 1 and a second ring 2), a gear 3 (a first mounting member), a retaining ring 4 (a second mounting member), a bearing 5 and a shaft 6.

In this embodiment, as shown in FIG. 2A and FIG. 2B , the installation and fixing mechanism for the shaft includes a first ring 1 and a second ring 2 assembled together, and the second ring 2 is located on one axial side of the first ring 1 .

As shown in FIGS. 3A to 3C , the first ring 1 has a C-shape, that is, the first ring 1 extends continuously along the circumferential direction and is formed with a notch 1c. One axial side surface of the first ring 1 is formed as a first inclined surface 11, which extends radially inwardly and obliquely toward one axial side, and is formed as a conical surface. The other axial side surface of the first ring 1 serves as a first side surface 14 against the gear 3 (first mounting member), and the first side surface 14 is perpendicular to the central axis of the shaft 6. The first ring 1 also includes a first inner peripheral surface 12 and a first outer peripheral surface 13 parallel to the central axis of the shaft 6.

Furthermore, in order to ensure that the first ring 1 can generate sufficient compression and elastic force in the subsequent assembly process, in the natural state (the state without any external force), the aperture of the first ring 1 is larger than the outer diameter of the shaft 6 by a predetermined value. In addition, as shown in FIG3C , the angle α between the first inclined surface 11 and the first inner peripheral surface 12 (the angle between the first inclined surface 11 and the central axis of the shaft 6) is, for example, 75 degrees, which is conducive to the first ring 1 realizing the so-called friction self-locking described below when the shaft assembly is in the working state.

As shown in FIGS. 4A to 4C , the second ring 2 has an O-shape, that is, the second ring 2 extends continuously along the entire circumference. The other axial side surface of the second ring 2 is formed as a second inclined surface 21, which extends toward the radial inner side while extending obliquely toward one axial side, and the second inclined surface 21 is formed as a conical surface. The second inclined surface 21 and the first inclined surface 11 abut against each other. An axial side surface of the second ring 2 is used as a second side surface 24 abutting against the snap ring 4 (second mounting member), and the second side surface 24 is perpendicular to the central axis of the shaft 6. The second ring 2 also includes a second inner peripheral surface 22 and a second outer peripheral surface 23 parallel to the central axis of the shaft 6.

Furthermore, the second ring 2 can achieve clearance fit or transition fit, or even interference fit with the shaft 6. In addition, as shown in FIG4C , the angle β between the second inclined surface 21 and the second inner peripheral surface 22 (the angle between the second inclined surface 21 and the central axis of the shaft 6) is, for example, 75 degrees, so that the second inclined surface 21 is in shape with the first inclined surface 11, and is conducive to the first ring 1 achieving the so-called friction self-locking described below when the shaft assembly is in the working state.

In this embodiment, as shown in FIG. 2A and FIG. 2B , the gear 3 is a helical gear. The inner circumferential surface of the gear 3 is formed with an internal spline protruding toward the shaft 6, and the outer circumferential surface of the shaft 6 is formed with an external spline protruding toward the gear 3. The internal spline and the external spline enable the gear 3 to be transmission-connected with the shaft 6, so that the torque from the shaft 6 can be output to the outside through the gear 3. In addition, the gear 3 and the shaft 6 can be assembled together by interference fit. In the axial direction A, the gear 3 is located between the bearing 5 and the mounting and fixing mechanism. The gear 3 abuts against the bearing 5 from one axial side, and the gear 3 abuts against the first side surface 14 of the first ring 1 of the mounting and fixing mechanism from the other axial side.

In this embodiment, as shown in FIG. 2A and FIG. 2B , the snap ring 4 is formed in an annular shape and has a notch, so that the snap ring 4 is formed in a C-shape. The shaft 6 is formed with an annular groove 6c that cooperates with the snap ring 4, and the width of the annular groove 6c is greater than the width (or thickness) of the snap ring 4. The snap ring 4 can be sleeved in the annular groove 6c, and the snap ring 4 is located in the annular groove 6c and abuts against the axial side wall of the annular groove 6c. The snap ring 4 protrudes from the annular groove 6c, and the snap ring 4 abuts against the second side surface 24 of the second ring 2 of the mounting and fixing mechanism from the axial side.

In this embodiment, as shown in Fig. 2A and Fig. 2B, the bearing 5 may be a radial bearing such as a ball bearing. The inner ring of the bearing 5 is located between the shaft shoulder 6s of the shaft 6 and the gear 3, and the inner ring of the bearing 5 abuts against the shaft shoulder 6s and the gear 3. The outer ring of the bearing 5 may be used to be fixed to the housing of the motor.

In this embodiment, as shown in FIG. 2A and FIG. 2B , the shaft 6 extends linearly along the axial direction A, and the outer peripheral surface of the shaft 6 is formed with a stepped shaft shoulder 6s and a recessed annular groove 6c, and the annular groove 6c is positioned at the shaft shoulder 6s on one side of the axial direction. As described above, the shaft shoulder 6s is used to cooperate with the retaining ring 4 to axially limit other components, and the annular groove 6c is used to install the retaining ring 4.

The following describes a method for installing a shaft assembly according to an embodiment of the present application.

As shown in FIG. 2B , FIG. 5A and FIG. 5B , a method for installing a shaft assembly according to an embodiment of the present application includes the following steps:

Mount the bearing 5 on the shaft 6 so that the inner ring of the bearing 5 abuts against the shaft shoulder 6s from one axial side;

Referring to FIG5A , the gear 3 is mounted on the shaft 6, so that the gear 3 and the shaft 6 are connected in transmission through spline cooperation and the gear 3 abuts against the inner ring of the bearing 5 from one axial side;

5A , the first ring 1 is mounted on the shaft 6 so that the first ring 1 abuts against the gear 3 from one axial side, and the first ring 1 is compressed in the radial direction R so that the first ring 1 is in a compressed state in which the first inner circumferential surface 12 thereof contacts the outer circumferential surface of the shaft 6, and the first ring 1 is maintained in the compressed state;

5B , the second ring 2 is mounted on the shaft 6 so that the second inclined surface 21 of the second ring 2 abuts against the first inclined surface 11 of the first ring 1 ;

5B , the snap ring 4 is mounted on the shaft 6 so that the snap ring 4 is assembled in the annular groove 6 c of the shaft 6 ; and

Referring to FIG. 5B , the first ring 1 is released (i.e., the compression state of the first ring 1 is released), and the first ring 1 is expanded in the radial direction R so that the first inner peripheral surface 12 of the first ring 1 is out of contact with the outer peripheral surface of the shaft, thereby making the second ring 2 abut against the retaining ring 4 from the other axial side and the second ring 2 can also define the shape of the first ring 1 after expansion, thereby making the retaining ring 4 abut against the side wall of the annular groove 6c on one axial side.

By adopting the above technical solution, the components sleeved on the shaft 6 in the shaft assembly according to the present application can maintain the same shape in various states and eliminate undesired axial movement.

When the shaft assembly is in a stationary state, it can be understood that the axial clearance between the components sleeved on the shaft 6 can be reduced to zero by installing the fixing mechanism, and all structures stably support each other, so that the components sleeved on the shaft 6 can maintain a stable stationary state.

When the shaft assembly is in a rotating state and the gear 3 does not generate additional axial force on the first ring 1 due to reasons such as changes in the torque transmission direction, all components on the shaft 6 will generate centrifugal force. At this time, there is no gap between the components, so the components generate forces to support each other. It can be understood that for other components with an overall annular shape and no gaps (such as the second ring 2, the gear 3, the bearing 5, etc.), the inner circumferences of these components are in a limited relationship with the outer circumference of the shaft 6, so that these components will not deform or move in other directions when the shaft rotates. For the first ring 1 with a gap 1c, its first inner circumference 12 is spaced from the outer circumference of the shaft 6, so there is a possibility of deformation in the radial direction R. However, as shown in FIG5B, when the first ring 1 is subjected to the centrifugal force F1, the following forces are mainly generated on the first ring 1 through other components: the first pressure F2 generated by the second ring 2 on the first ring 1, the direction of the first pressure F2 is perpendicular to the first inclined surface 11; the second pressure F3 generated by the gear 3 on the first ring 1, the direction of the second pressure F3 is perpendicular to the first side surface 14 of the first ring 1. The first pressure F2 and the second pressure F3 can maintain a balance with the centrifugal force F1 , so that the first ring 1 will not be deformed in the radial direction R when rotating with the shaft 6 .

When the shaft assembly is in a rotating state and the gear 3 generates an additional axial force on the first ring 1 due to the change in the torque transmission direction, as shown in FIG5C , the following forces mainly act on the first ring 1: the first pressure F2 generated by the second ring 2 on the first ring 1, the direction of the first pressure F2 is perpendicular to the first inclined surface 11; the second pressure F3 generated by the gear 3 on the first ring 1, the direction of the second pressure F3 is perpendicular to the first side surface 14 of the first ring 1; the friction force F4 generated between the first ring 1 and the second ring 2, the direction of the friction force F4 is along the first inclined surface 11. When the angle between the first inclined surface 11 and the first inner peripheral surface 12 of the first ring 1 (that is, the angle between the first inclined surface 11 and the central axis of the shaft 6) is α, according to the definition of friction force, F4＝μ×F2 is satisfied; according to the force balance principle of the first ring 1 in the state of rotating with the shaft 6, F4＝tan(90°-α)×F2 is satisfied. It can be seen that when μ>tan(90°-α), the so-called friction self-locking can be achieved. That is to say, no matter how large the axial force (second pressure F3) generated by the gear 3 on the first ring 1 is, the first ring 1 will neither be radially deformed nor move axially when rotating with the shaft 6 .

It is understood that the size of the first ring 1 can be set so that the diameter of the first ring 1 in the natural state is slightly larger than the diameter of the first ring 1 in the installed or used state, so that, in the installed state shown in FIG. 5B , the first ring 1 still has a tendency to expand or is in a certain compression state. In this way, it is ensured that the axial clearance between the components is eliminated. In addition, it is understood that when the shaft assembly rotates, due to the centrifugal force, the first ring 1 tends to expand (the diameter becomes larger), which can also ensure that the axial clearance between the components is eliminated.

The present application is not limited to the above-mentioned embodiments, and those skilled in the art can make various modifications to the above-mentioned embodiments of the present application under the guidance of the present application without departing from the scope of the present application. The following is a supplementary explanation.

i. It is understood that the mounting and fixing mechanism of the present application is not limited to the application scenarios described in the above specific embodiments, but can be applied to different components that need to be relatively fixed to the shaft in the axial direction as needed. For example, the shaft assembly of the present application can be applied to motors, transmissions, etc.

ii. The angle α between the first inclined surface 11 and the first inner peripheral surface 12 (the angle between the first inclined surface 11 and the central axis of the shaft 6) and the angle β between the second inclined surface 21 and the second inner peripheral surface 22 (the angle between the second inclined surface 21 and the central axis of the shaft) can both be 75 degrees or greater than 75 degrees. At the same time, both the angle α and the angle β are less than 90 degrees.

iii. The mounting and fixing mechanism of the present application can play a role in fixing and limiting other components installed on the shaft, and can eliminate the installation gap between the components. It can also avoid the problem of NVH performance degradation caused by axial movement of components when there is a gap.

Claims

A mounting and fixing mechanism for a shaft, used to be sleeved between a first mounting member and a second mounting member in the axial direction (A) of the shaft (6), wherein both the first mounting member and the second mounting member are sleeved on the shaft (6), and the mounting and fixing mechanism comprises:

a first ring (1), which continuously extends along the circumference of the shaft (6) and is formed with a notch (1c); the aperture of the first ring (1) in a natural state is larger than the outer diameter of the shaft (6); one axial side surface of the first ring (1) is formed as a first inclined surface (11); the first inclined surface (11) extends radially inwardly and obliquely toward one axial side; the other axial side surface (14) of the first ring (1) is used to abut against the first mounting member; and

A second ring (2) extends continuously along the entire circumference of the shaft (6); the other axial side surface of the second ring (2) is formed as a second inclined surface (21) that matches the shape of the first inclined surface (11) and abuts against it; and an axial side surface (24) of the second ring (2) is used to abut against the second mounting member.
The installation and fixing mechanism for a shaft according to claim 1 is characterized in that an angle (α) formed by the first inclined surface (11) and the central axis of the shaft (6) is equal to an angle (β) formed by the second inclined surface (21) and the central axis.
The installation and fixing mechanism for a shaft according to claim 1 or 2 is characterized in that 90 degrees>α≥75 degrees.
The installation and fixing mechanism for a shaft according to any one of claims 1 to 3 is characterized in that:

The side surface (14) of the first ring (1) for abutting against the first mounting member is perpendicular to the central axis of the shaft (6); and/or

The side surface (24) of the second ring (2) for abutting against the second mounting member is perpendicular to the central axis of the shaft (6).
The installation and fixing mechanism for a shaft according to any one of claims 1 to 4, characterized in that:

The inner circumference (12) of the first ring (1) and the inner circumference (22) of the second ring (2) are parallel to the central axis of the shaft (6); and/or

The outer peripheral surface (13) of the first ring (1) and the outer peripheral surface (23) of the second ring (2) are parallel to the central axis of the shaft (6).
The installation and fixing mechanism for a shaft according to any one of claims 1 to 5 is characterized in that the angle between the first inclined surface (11) and the central axis of the shaft (6) is α and the friction coefficient between the first inclined surface (11) and the second inclined surface (21) is μ, satisfying μ>tan(90°-α).
A shaft assembly comprises the shaft mounting and fixing mechanism according to any one of claims 1 to 6, the shaft (6), the first mounting member and the second mounting member.
The shaft assembly according to claim 7 is characterized in that the first mounting member is a gear (3), the second mounting member is a retaining ring (4), the shaft (6) is formed with an annular groove (6c) for mounting the retaining ring (4), and the width of the annular groove (6c) is greater than the width of the retaining ring (4).
The shaft assembly according to claim 8 is characterized in that it further comprises a bearing (5), the shaft (6) is formed with a shaft shoulder (6s), and the bearing (5) is located between the shaft shoulder (6s) and the gear (3).
A method for installing a shaft assembly according to any one of claims 7 to 9, comprising:

Sleeve the first mounting member onto the shaft (6);

The first ring (1) is fitted onto the shaft (6), so that the first ring (1) abuts against the first mounting member from one axial side, and the first ring (1) is compressed in the radial direction (R) and maintained in a compressed state;

The second ring (2) is mounted on the shaft (6) so that the second inclined surface (21) of the second ring (2) abuts against the first inclined surface (11) of the first ring (1);

Sleeve the second mounting member onto the shaft (6); and

The compressed state of the first ring (1) is released, so that the first ring (1) expands in the radial direction (R), thereby causing the second ring (2) to abut against the second mounting member from the other side in the axial direction.