JP2615990B2 - Ring attachment device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to an annular body having a different coefficient of linear expansion between an annular body such as an inner ring and an outer ring of a bearing and a mating member to which the annular body is attached. It relates to a mounting device.

[Conventional technology]

Conventionally, for example, a report on a mounting structure in a case where the linear expansion coefficient of a rolling bearing is different from that of a mating member to which the rolling bearing is attached has been published in LUBRICATION ENGINEERIG July 1981, 407-41.
It is listed on page 5.

In this rolling bearing, as shown in FIG. 3, a cylindrical roller 5 with a retainer 6 is arranged between an inner ring 2 attached to a shaft 1 and an outer ring 3 attached to a shaft box (not shown). The shaft 1 is made of a steel material, and the inner ring 2 is made of a ceramic material. Both end surfaces in the axial direction of the inner ring 2 are tapered surfaces that expand outwardly with respect to the center axis,
Are fitted by a loose fit. Both end surfaces of the inner ring 2 are clamped by a pair of spacers 4 made of a steel material fitted to the shaft 1 by interference fitting.
When thermal expansion occurs, the inner ring 2 and the spacer 4 slide relatively on the clamping surface so that an excessive load is not applied.

[Problems to be solved by the invention]

In the above-mentioned rolling bearing, the load applied to the bearing is enlarged by the wedge action of the both end faces of the inner ring 2 and transmitted to the spacer 4, so that the contact surface pressure on the both end faces of the inner ring 2 is remarkably increased, resulting in wear. In some cases, inconveniences such as breakage or breakage due to the limit of the applied load may occur, and the upper limit of the applied load is limited to a small value.

Further, when the inner ring 2 and the spacer 4 are assembled to the shaft 1, a relative slip occurs between the inner ring 2 fitted with the clearance fit and the spacer 4 fitted with the interference fit. However, accurate centering is difficult, and the assembling work requires skill, and there is a problem in workability.

SUMMARY OF THE INVENTION The present invention solves the above-mentioned problems, and is less likely to cause abrasion, breakage, etc. of the annular body during operation use of the annular body having a different linear expansion coefficient from that of the mating member. It is an object of the present invention to provide a mounting device capable of easily performing an assembling operation.

[Means for Solving the Problems] In order to achieve the above object, in the present invention, the annular body fitted to the outer or inner periphery of the mating member has a linear expansion coefficient different from that of the mating member, Both sides of the annular body in the axial direction are supported by a pair of spacers that are fitted to the peripheral surface of the annular body opposite to the mating surface with the mating member and firmly engaged with the outer or inner circumference of the mating member. Wherein the spacer has a coefficient of linear thermal expansion in a radial direction from a portion in contact with a mating member to a portion in contact with an annular body, and a change in a coefficient of linear thermal expansion in a radial direction caused by the mating member and the annular body. And a material which changes continuously or stepwise in the radial direction with the same direction as the above.

As a material whose linear expansion coefficient changes continuously,
For example, a composite material composed of a ceramic material and a metal material is used, and as the material in which the linear expansion coefficient of the spacer changes stepwise, for example, a material obtained by laminating a plurality of materials having different linear expansion coefficients in a radial direction is used. I do.

It is preferable that the linear expansion coefficient of the spacer is set to a coefficient of linear expansion substantially equal to that of the mating member at a portion contacting the mating member, and to a coefficient of expansion substantially equal to that of the annular member at a portion contacting the annular body.

The fitting surface of the annular body to the mating member is in a firmly fitted state at the latest when the annular body is in operation, and the load applied to the annular body and the maximum stress due to this fitting and temperature change are reduced by the configuration of the annular body. It is advantageous to set the dimensions such that they are smaller than the allowable maximum stress of the material.

Alternatively, at least one end face in the axial direction of the annular body may be formed as a tapered surface, and an intermediate spacer having an opposite end face having the same taper angle as the annular body may be sandwiched between the annular body and the spacer. Good. The peripheral surface of the intermediate spacer opposite to the mating surface with the mating member may be firmly engaged with the spacer or integrally fixed thereto.

When a tapered surface is formed at the axial end surface of the annular body, it is preferable that the taper angle is set so that a predetermined relationship is established with respect to the axial length and the diameter at the center of the thickness of the annular body.

When the present invention is applied to the mounting of a bearing ring of a rolling bearing, the axial end of the spacer can be used also as a guide collar for a rolling element of the rolling bearing, and a guide ring for the retainer of the rolling element. Can be shared.

[Action]

The annular body attached to the mating member by the mounting device of the present invention transmits the load applied to the annular body to the mating member via the spacer fitted to the annular body.

Since the linear expansion coefficient of the spacer has a radial direction that changes in accordance with the linear expansion coefficient between the mating member and the annular body even if a temperature change occurs between the time of mounting the annular body and the time of operation use. The amount of change in the state of engagement of the spacer with respect to the mating member or the state of engagement of the annular pair is absorbed by the spacer, and the interference of the spacer with respect to the annular body is kept substantially constant. For this reason,
The load applied to the annular body is effectively transmitted to the mating member via the spacer.

In particular, when the linear expansion coefficient of the portion of the spacer that is in contact with the mating member is substantially equal to that of the mating member, and the linear expansion coefficient of the portion of the spacer that is in contact with the annular body is set to a value substantially equal to that of the annular member, the temperature change The fitting state of the spacer to the annular body does not fluctuate between before and after, and a certain interference can be reliably held.

The fitting surface of the annular body to the mating member is in a firmly fitted state at the latest at the time of operation use of the annular body, and the load applied to the annular body and the maximum stress due to this fitting and the temperature change are reduced by the material of the annular body. When the dimensions of the fitting surface are set so as to be smaller than the allowable maximum stress, the load applied to the annular body is transmitted to the mating member while being shared by the annular body and the spacer. It is not destroyed by the applied load.

When a tapered surface is formed on the axial end surface of the annular body and an intermediate spacer having an opposite end surface having the same taper angle is interposed between the tapered surface and the spacer, the applied load is It can be shared between the intermediate spacer and the annular body, the spacer and the intermediate spacer.

Further, when the angle of the tapered surface formed on the axial end surface of the annular body is set so that a predetermined relationship is established with respect to the axial length and the diameter at the center of the thickness of the annular body, the annular shape is changed by the temperature change. The effect of thermal stress on the body can be prevented.

〔Example〕

 Hereinafter, embodiments of the present invention will be described with reference to the drawings.

FIG. 1 shows an inner ring (annular body) of a cylindrical roller bearing according to the present invention.
This is an embodiment in which the present invention is applied to the assembling of a shaft and a shaft (a mating member).
The cylindrical roller bearing shown in FIG. 1 includes an inner ring 20, an outer ring 30, and a cylindrical roller 50 held and guided by a retainer 51 between the inner ring 20 and the outer ring 30.

The inner peripheral side fitting surface 21 of the inner ring 20 is fitted to the shaft 10 by clearance fit, and the vertical surfaces formed on both axial end surfaces 22 of the inner ring 20 are supported by a pair of spacers 40. It is attached in the state.

Each spacer 40 has an annular portion 40a fitted on the outer peripheral surface of the shaft 10,
A cylindrical portion 40b protruding in the axial direction from the annular portion 40a and fitted to the outer peripheral side fitting surface 23 at the end of the inner ring 20; if the inner periphery 42 of the annular portion 40a is tight with respect to the shaft 10, Mating,
Alternatively, the inner peripheral surface 43 of the cylindrical portion 40b is fitted to the inner ring 20 by firmly engaging by bonding, welding, screw fastening, or the like.

The end surfaces 22 on both sides of the inner race 20 and the opposing end surfaces of the spacer 40 are not limited to the case where they are brought into contact with each other, and may be made to face each other via an appropriate axial clearance.

The constituent material of the inner ring 20 of the cylindrical roller bearing is, for example, a ceramic material such as silicon nitride, and the constituent material of the shaft 10 is a steel material. Therefore, the linear expansion coefficient α _j of the inner ring 20 is
Is smaller than the coefficient of linear expansion α _s . The constituent material of the outer ring 30 is bearing steel.

Further, the spacer 40, the linear expansion coefficient of the radially extending from the inner peripheral portion fitted to the shaft 10 in the mated outer peripheral portion to the inner ring 20, the linear expansion coefficient alpha _s and the inner ring 20 of the shaft 10 Coefficient of linear expansion α _j
And a material that changes in the radial direction in the same direction as the change in the radial direction.

The linear expansion coefficient of the spacer 40 in the radial direction may change continuously or may change stepwise. As a material whose linear expansion coefficient continuously changes, for example, a composite material (functionally graded material) in which the mixing ratio of the ceramic material and the metal material is different in the radial direction can be used, and the linear expansion coefficient changes stepwise. As the material, for example, a laminated material in which at least two materials having different linear expansion coefficients are overlapped in the radial direction by fitting, bonding, or the like can be used.

In case of constituting the spacer 40 by using the materials described above, the linear expansion coefficient of the inner peripheral portion including an inner peripheral surface 42 of the annular portion 40a of the spacer 40 substantially in the linear expansion coefficient alpha _s of the shaft 10 The linear expansion coefficient of the outer peripheral portion including the inner peripheral surface 43 of the cylindrical portion 40b of the spacer 40 is set substantially equal to the linear expansion coefficient α _j of the inner ring 20, and the inner peripheral portion extends from the inner peripheral portion to the outer peripheral portion. It is preferable that the linear expansion coefficient of the intermediate portion is set so as to change continuously or stepwise and to decrease gradually.

Next, the shaft 10 when the temperature T _b at the time of use of cylindrical roller bearings of the structure is higher than the temperature T _a during mounting, the inner ring 20
And a load transmission mechanism between the spacers 40 will be described.

Now, when mounting the bearing, it is assumed that the inner ring 20 and the shaft 10 have a loose fit, the spacer 40 has a close fit with respect to the shaft 1 and the inner ring 200, respectively, and the shaft 10 is made of steel (linear expansion coefficient α _s ). The inner ring 20 is made of a ceramic material (linear expansion coefficient α _j ),
Is a composite material or a laminated material, in which the linear expansion coefficient α _k1 of the inner peripheral portion in contact with the shaft 10 is substantially equal to the linear expansion coefficient α _s of the shaft 10, and the linear expansion coefficient α _k0 of the outer peripheral portion in contact with the inner ring 20. Is an inner ring
It is assumed that the linear expansion coefficient α _j is substantially equal to 20.

When the clearance between the inner ring 20 and the shaft 0 at the time of mounting the bearing is Δd, the interference between the spacer 40 and the shaft 10 is Δδ, and the interference between the spacer 40 and the inner ring 20 is ΔD. in the clearance fit with respect to the axis 10 of the inner ring 200 will become _{Δd- (α s -α j) (} T b -T a) d, white accounted for shaft 10 of the spacer 40, Δδ + (α _s - α _k1 ) (T _b −T _a ) d, and the interference between the spacer 40 and the inner ring 20 changes to ΔD + (α _j −α _k0 ) (T _b −T _a ) D. Can be

The amount of change between these fits and the interference is influenced in relation to each other, but the amount of change of the fit between the inner ring 20 and the shaft 10 (α _s −α _j ) (T _b −T _a ) If d is set to be smaller than the clearance Δd at the time of mounting, even if the clearance of the inner ring 20 fitted to the shaft 10 changes, the clearance between the shaft 10 of the spacer 40 and the inner ring 20 is thereby changed. It can be considered that interference is rarely affected.

Then, the amount of interference (α _s −α _k1 ) (T _b −T _a ) d of the interference of the _spacer 40 with respect to the axis 10 is a value close to zero because α _s ≒ α _k1. Similarly, the amount of _interference (α _j −α _k0 ) (T _b −T _a ) D of the _{interference with} respect to the inner ring 20 of the seat 40 is close to zero because α _j ≒ α _k0. Interference Δd when mounting 40 on shaft 10 and inner ring 20
And ΔD are kept substantially constant before and after the temperature change even if the temperature rises during use.

Actually, the amount of change in the interference (or clearance) affects each other, but since the linear expansion coefficient of the spacer 40 is configured to have the directionality as described above, the temperature T _a from the size of the linear expansion coefficient alpha _k of the spacer so as to close to zero the sum of the changes in Hamagodai fitting surface 42 and 43 due to changes in T _b, and the degree of radial change such If selected, the interference ΔD can be kept substantially constant.

Accordingly, the load applied to the bearing can be effectively transmitted to the shaft 10 by the spacer 40 via the outer peripheral side fitting surface 23 of the inner ring 20.

In the above embodiment, the inner ring 20 has a loose fit with respect to the shaft 10 during the mounting and use of the bearing, but the temperature difference between the mounting and the use and the inner ring 20 and the shaft 10 Depending on the difference in the coefficient of linear expansion, the shaft 10
May be configured so as to have a tight fitting state with interference. In this case, the maximum tensile stress σ _{tmax at} the inner peripheral side fitting surface 21 of the inner ring 20, that is, the maximum tensile stress due to _{interference with} the shaft 10, the maximum tensile stress due to the load applied to the bearing, The sum of the compressive stress due to the interference at the side fitting surface 23 becomes smaller than the allowable tensile stress σ _T of the constituent material of the inner ring 20 and the outer fitting surface 23 of the inner ring 20.
, The maximum compressive stress due to the _{interference with the spacer} 40, the maximum compressive stress due to the load applied to the shaft 10, and the tension due to the interference at the inner peripheral side fitting surface 21 of the inner ring 20. It is preferable to set the dimensions of the fitting surfaces 21, 23 of the inner ring 20 so that the sum of the stress and the stress is smaller than the allowable compressive stress σ _C of the constituent material of the inner ring 20.

With such a configuration, when the temperature T _b at the time of use of the bearing rises above the temperature T _a during installation, but white tighten against the inner ring 20 of the spacer 40, white accounted for shaft 10 of the spacer 40 and ,
The interference between the inner ring 20 and the shaft 10 is influenced by the interference, but since the linear expansion coefficient of the spacer 40 has a directionality that changes in the radial direction as described above, the interference of the spacer 40 with respect to the shaft 10 is required. (Α _s −α _k1 ) (T _b −T _a ) d
And a spacer generated by interference between the inner ring 20 and the shaft 10
The sum of the amount of change of interference with respect to the axis 10 of 40 is the spacer 40
Becomes a value close to zero by being absorbed by the internal distortion of. For this reason, the interference ΔD of the spacer 40 with respect to the inner ring 20 set at the time of mounting the bearing is kept substantially constant before and after the temperature change even if the interference Δδ with respect to the shaft 10 changes.

Thus, the load applied to the bearing is divided into a portion transmitted to the shaft 10 through the spacer 40 and a portion transmitted directly to the shaft 10 through the inner peripheral side fitting surface 21 of the inner race 20. Compared to the case of the above embodiment in which the load is transmitted only through the seat 40,
Since the shared load via the spacer 40 of the inner ring 20 is reduced, the allowable maximum load of the bearing is increased by that amount, or the allowable tensile stress σ _T and the allowable compressive stress σ _C of the inner ring 20 are reduced. Accordingly, the total transmittable load can be maximized by optimizing the load transmitted by each of the fitting surfaces 21 and 23.

Even if the bearing load is shared by the inner ring 20,
So that the maximum tensile stress and the maximum compressive stress of the respective mating surfaces 21 and 23 are smaller than the respective maximum allowable stresses of the constituent materials.
Is set, the inner ring 20 is not broken.

In this circumferential roller bearing, the cylindrical portion of the spacer 40
The end face of the axial end 41 of the cylindrical roller 40b is closely opposed to the end face of the cylindrical roller 50, and also functions as a guide flange of the cylindrical roller 50. Further, the outer diameter of the axial end 41 is the inner diameter of the retainer 51. , And also functions as a guide wheel of the retainer 51.
These functions may be used for only one of them.

In the above embodiment, the linear expansion coefficient α
_{The case where k1} is set substantially equal to the coefficient of linear expansion α _s of the shaft 10 and the coefficient of linear expansion α _k0 of the outer peripheral side portion is set almost equal to the coefficient of linear expansion α _j of the inner ring 20 has been described. However, regarding the value of the coefficient of linear expansion of each part from the inner peripheral part to the outer peripheral part and the rate of change of the coefficient of linear expansion in the radial direction, the temperature difference between when the bearing is mounted and when it is used, the inner ring 20 Can be appropriately selected so as to have an optimum value and a predetermined direction according to the difference in linear expansion coefficient between the shaft and the shaft 10 and the dimensions and the conditions for mounting the inner ring 20 and the spacer 40 to the shaft 10. it can.

FIG. 2 shows an embodiment in which the present invention is applied to assembling an inner ring (annular body) of a ball bearing and a shaft (a mating member). The ball bearing shown in FIG. 1 includes an inner ring 20, an outer ring 30, and a ball 53 that is held and guided by a retainer 54 between the inner ring 20 and the outer ring 30. The inner ring 20 is fitted with a clearance fit.
A pair of spacers 40 that firmly engage with 10 are fitted by an interference fit. The constituent materials of the shaft 10, the inner ring 20, and the spacer 40 are the same as those of the cylindrical roller bearing of FIG.

In this embodiment, both end surfaces 22 in the axial direction of the inner ring 20 are formed in a tapered surface having an inclination angle of θ ₁ , θ ₂ with respect to a cross section perpendicular to the axis, the diameter of which expands in an outward opening direction with respect to a center axis. A pair of intermediate spacers 45 having opposing facing surfaces having the same inclination angle as the both end surfaces 22 are firmly engaged with the shaft 10 and disposed between the inner ring 20 and the spacer 40, and the inner ring 20 is sandwiched. The intermediate spacer 45 is made of a material having a linear expansion coefficient equivalent to that of the shaft 10.

In the ball bearing having the above-described configuration, the load applied to the bearing is not only shared by the spacer 40 via the outer peripheral side fitting surface 23 of the inner ring 20 but also via the both end surfaces 22 of the inner ring 20. Since the load shared by the intermediate spacer 45 can be transmitted to the shaft 10, the shared load of the inner ring 20 is reduced as compared with the case where the load is transmitted only by the spacer 40.

In this embodiment, the inner peripheral side fitting surface of the inner ring 20 is also used.
21 becomes a firmly fitted state with interference at the latest when the bearing is used with respect to the shaft 10, and the maximum tensile stress and the maximum compressive stress of the inner ring 20 become smaller than each allowable maximum stress of the constituent material As described above, the dimensions of the fitting surfaces 21 and 23 may be set. With this configuration, the load applied to the bearing can be transmitted to the shaft 10 even through the inner peripheral side fitting surface 21 of the inner ring 20, so that the spacer 40 and the intermediate spacer 45 As compared with the case where the load is transmitted through the inner ring 20, the shared load of the inner ring 20 is further reduced.

In this embodiment, when the inclination angles θ ₁ , θ ₂ of both end surfaces 22 of the inner ring 20 are set as follows, the distance between the inner ring 20 and the intermediate portion due to a temperature change between when the bearing is mounted and when the bearing is used. seat
The effect of thermal stress generated on the contact surface between the shaft 45 and the fitting surface between the inner ring 20 and the shaft 10 can be prevented.

The axial length at the center of thickness of the inner ring 20 is W _P , and the diameter is
Assuming that D _P , the axial length changes Δx ₁ , Δx ₂ and the radial length changes Δy ₁ , Δy ₂ of the both end surfaces 22 due to the temperature change ΔT are obtained by the following equations.

The condition when the relative length due to the temperature change does not occur in the axial direction and the radial direction of the inner ring 20 is given by the following equation.

Then, _assuming α _s ≠ α _j , ΔT ≠ 0, the above equation (1),
Solving (2) and (3) yields tan θ ₁ + tan θ ₂ = 2W _P / D _P (4).

Θ ₁ and θ _{2 in the} above formula are positive when both end surfaces of the inner ring 20 are tapered surfaces that expand in the outward opening direction as shown in the drawing, and conversely, taper surfaces that decrease in the inner opening direction. Is negative if.

When the intermediate spacer 45 of this embodiment is provided, only one axial end face of the inner ring 20 may be clamped.

In addition to the illustrated case, the intermediate spacer 45 may be attached to the shaft 10 by firmly engaging the intermediate spacer 45 with the shaft 10 and then tightly fitting the spacer 40 on the outer peripheral surface of the intermediate spacer 45 by fitting. Alternatively, a material in which the intermediate spacer 45 and the spacer 40 are joined and fixed integrally may be used.

In each of the above embodiments, the case where the inner ring made of a ceramic material is attached to a shaft made of a steel material has been described, but the present invention is not limited to such a case. For example, the inner ring made of a steel material may be made of stainless steel, brass, aluminum alloy, or the like. The same can be applied to the case of mounting on a shaft made of the above material.

Further, the present invention is applicable not only to bearings having different coefficients of linear expansion between the inner ring and the shaft, but also to bearings having different coefficients of linear expansion between the outer ring and the shaft box.

The present invention can be applied not only to the case where the temperature during use of the bearing is higher than the temperature at the time of mounting, but also to the case where the temperature during use is lower than when the bearing is mounted.

Further, the present invention can be applied not only to a rolling bearing but also to a case where an annular body which is a component of a sliding bearing or other device is attached to a counterpart member having a different linear expansion coefficient.

〔The invention's effect〕

As described above, according to the present invention, when the linear expansion coefficient of the annular body is different from that of the mating member, the load applied to the annular body is changed via the spacer fitted to the annular body. Even if the engagement state of the spacer to the mating member or the fitting state of the annular body to the mating member changes due to a temperature difference between the time of attachment and the time of use, these changes Can be absorbed by the internal strain of the spacer whose linear expansion coefficient changes in the radial direction, and the interference of the spacer with respect to the annular body can be kept substantially constant before and after the temperature change.
Therefore, the load transmission by the spacer is effectively performed as originally designed, and the upper limit of the transmittable load can be easily increased.

Further, according to the present invention, the applied load is not only applied to the spacer, but also to the fitting surface between the annular body and the mating member, or in addition to the intermediate space for clamping the tapered axial end surface of the annular body. When the configuration is such that the transmission can also be performed by the seat, not only the load capacity of the annular body is further increased, but also by setting the angle of the tapered surface formed on the axial end face of the annular body to a predetermined angle, the temperature can be increased. It is also possible to prevent the concentration of thermal stress due to the change.

Further, according to the present invention, the clearance between the annular body and the mating member can be reduced, so that not only the centering at the time of mounting is facilitated but also the concentricity with the mating member at the time of driving use is improved. Since it can be held with high accuracy, the high performance of the attached device is maintained, and a highly reliable attachment device can be obtained.

[Brief description of the drawings]

FIG. 1 is an upper half vertical sectional side view showing an embodiment in which the present invention is applied to a cylindrical roller bearing. FIG. 2 is an upper half vertical side view showing an embodiment in which the present invention is applied to a ball bearing. FIG. 3 is an upper half vertical sectional side view showing a mounting state of a conventional cylindrical roller bearing. In the figure, reference numeral 10 denotes a shaft (a mating member), 20 denotes an inner ring (annular body), 21 denotes an inner peripheral side fitting surface of the inner ring, 22 denotes an axial end face of the inner ring, 23 denotes an outer peripheral side fitting surface of the inner ring, and 40 denotes The spacer, 42 is a fitting surface of the spacer to the shaft, 43 is a fitting surface of the spacer to the inner ring, and 45 is an intermediate spacer.

Claims (6)

(57) [Claims] An annular body fitted to the outer or inner periphery of a mating member has a different linear expansion coefficient than the mating member, and a peripheral surface of the annular body opposite to a fitting surface with the mating member. And a pair of spacers that firmly engage the outer periphery or inner periphery of the mating member to support both end faces in the axial direction of the annular body, wherein the spacer is attached to the mating member. A material in which the coefficient of linear expansion in the radial direction from the contacting part to the part in contact with the annular body changes continuously or stepwise in the radial direction in the same direction as the change in the coefficient of linear thermal expansion in the radial direction due to the mating member and the annular body. A mounting device for an annular body, comprising: 2. A portion of the spacer that contacts the counterpart member has a linear expansion coefficient substantially equal to that of the counterpart member, and a portion of the spacer that contacts the annular body has a coefficient of linear expansion approximately equal to the annular member. (1) A mounting device for an annular body according to (1). 3. The fitting surface of the annular body with respect to the mating member is in a firmly fitted state at the latest when the annular body is used for operation.
And (1) a dimension set so that the load applied to the annular body and the maximum stress due to the fitting and the temperature change are smaller than the allowable maximum stress of the constituent material of the annular body. (2) A mounting device for an annular body according to (2). 4. The annular body has at least one end face in the axial direction which is a tapered face, and an intermediate spacer having an opposite end face having the same angle as the tapered face is sandwiched between the annular body and the spacer. Item 8. The mounting device for an annular body according to any one of Items (1) to (3). 5. The thickness of the annular body, wherein the angles θ ₁ , θ ₂ of both axial end surfaces of the annular body with respect to a cross section perpendicular to the axis are positive when the center is opened outward and negative when the center is open. The annular body mounting device according to claim 4, wherein the axial length W _P at the thickness center and the diameter D _P are set to have a relationship represented by tan θ ₁ + tan θ ₂ = 2 W _P / D _P. . 6. An annular body is a bearing ring of a rolling bearing, and an axial end of a spacer fitted to the bearing ring has at least one of a function as a guide collar for a rolling element and a guide wheel for a retainer. The mounting device for an annular body according to any one of claims (1) to (5), comprising: