JPH02253010A - Ring member attaching device - Google Patents

Abstract

PURPOSE:To prevent a ring member from being damaged, by forming a spacer from a material having a linear radial expansion coefficient which is effective in a range from a part making contact with the associated member to a part making contact with the ring member and which varies continuously and radially in a direction common to variations in the linear radial expansion coefficients of the associated member and the ring member. CONSTITUTION:A space 40 is formed of a material having a linear radial expansion coefficient which is effective in a range from its inner peripheral part fitted on a shaft 10 (associated member) to its outer peripheral part fitted in an inner race 20 (ring member) and which varies continuously and radially in a direction common to radial variations in the linear radial expansion coefficients of the shaft 10 and the inner race 20. The radial expansion coefficient of the spacer 40 continuously and steppedly varies. Accordingly, if the value of the linear expansion coefficient, the degree of variations in the radial direction and the like are selected in such a way that the sum of variations in interference between fitting surfaces 42, 43, due to a fact that the temperature of the bearing during use thereof is higher than that upon installation thereof, may be made to be approximately zero, the interference between the spacer 40 and the inner race 20 may be maintained at a substantially constant value, thereby it is possible to effectively transmit a load to the shaft 10 through the intermediary of the spacer 40.

Description

Detailed Description of the Invention [Industrial Field of Application] The present invention is directed to the improvement of annular bodies, such as the inner ring and outer ring of a bearing, when the linear expansion coefficients of the annular body and the mating member to which this annular body is attached are different. Relating to a mounting device.

[Conventional technology]

Previously, there had been a report on the mounting structure when the linear expansion coefficients of a rolling bearing and the mating member to which it is attached differ, for example, in the LUBRICATION ENGINEERTG.
198], July issue, pages 407-415.

As shown in FIG. 3, this rolling bearing consists of a cylindrical roller with a retainer 6 installed between an inner ring 2 mounted on a shaft 1 and an outer ring 3 attached to an axle box (not shown). 5 is arranged, the shaft 1 is made of steel material, and the inner ring 2 is made of ceramic material.

Both end surfaces in the axial direction of the inner ring 2 are tapered surfaces that expand outward in diameter with respect to the central axis, and are fitted onto the shaft 1 with a loose fit. Both end surfaces of the inner ring 2 are sandwiched between a pair of spacers 4 made of steel that are fitted onto the shaft 1 by interference fit, and when the spacer 1 and the spacer 4 thermally expand,
The inner ring 2 and the spacer 4 slide relative to each other on the clamping surfaces 2 to prevent excessive loads from being applied.

[Problem to be solved by the invention]

In the above-mentioned rolling bearing, the load applied to the bearing is magnified by the wedge action of both end faces of the inner ring 2, and
As a result, the contact pressure on both end faces of the inner ring 2 increases significantly, causing problems such as wear and damage, or failure when the load reaches its limit, and the upper limit of the applied load. There is a problem that it is restricted to a small value.

Furthermore, when assembling the inner ring 2 and spacer 4 onto the shaft 1, relative slippage occurs between the inner ring 2, which is fitted with a clearance fit, and the spacer 4, which is fitted with an interference fit. However, accurate centering is difficult and assembly requires skill, which poses a problem in terms of workability.

This invention solves the above problems, and makes it difficult for the annular body to be worn out or damaged during operation and use of the annular body, which has a linear expansion coefficient different from that of the mating member. The purpose is to provide a mounting device that can easily cause injury.

[Means for Solving the Problems] In order to achieve the above object, in the present invention, the annular body fitted on the outer periphery or the inner periphery of the mating member has a linear expansion coefficient different from that of the mating member, Both end surfaces of the annular body in the axial direction are supported by a pair of spacers that fit into the circumferential surface of the annular body on the opposite side of the mating surface with the mating member and firmly engage with the outer or inner circumference of the mating member. The spacer has a coefficient of linear expansion in the radial direction from a portion in contact with the mating member to a portion in contact with the annular body that is equal to the coefficient of linear expansion in the radial direction of the mating member and the annular body. It is constructed of a material that changes continuously or stepwise in the radial direction with a common zigzag direction.

For example, a composite material consisting of a ceramic material and a metal material is used as a material whose coefficient of linear expansion changes continuously, and a material whose linear expansion coefficient changes stepwise is, for example, a composite material made of a ceramic material and a metal material. It uses multiple materials with different coefficients laminated in the radial direction.

It is preferable that the coefficient of linear expansion of the spacer is set such that the portion in contact with the mating member has a linear expansion coefficient substantially equal to that of the mating member, and the portion in contact with the annular body is set to have a coefficient of expansion substantially equal to that of the annular body.

The fitting surface of the annular body with respect to the mating member is in a firmly fitted state at the latest during operation of the annular body, and the load applied to the annular body and the maximum stress due to this fitting and temperature change are determined by the configuration of the annular body. It is convenient to set the dimensions to be smaller than the maximum permissible width J of the material.

Alternatively, at least one end surface in the axial direction of the annular body may be formed into a tapered surface, and an intermediate spacer having an opposite end surface having the same taper angle as the annular body may be sandwiched between the annular body and the spacer. good. The circumferential surface of the intermediate spacer on the side opposite to the surface that engages with the mating member may be tightly engaged with the spacer or may be fixed integrally with the spacer.

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

When this invention is applied to the installation of a raceway shaft of a rolling bearing, the i+b direction end of the spacer can also be used as a guide collar for the rolling elements of the rolling bearing, and also as a guide ring for the cage of the rolling elements. can do.

[Operation] The annular body attached to the mating member by the attachment 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.

Even if the temperature changes between when the annular body is installed and during operation, the linear expansion coefficient of the spacer has a directionality that changes in the radial direction according to the linear expansion coefficient of the mating member and the annular body. Therefore, the amount of change in the stopping state of the spacer with respect to the mating member or the fitting state of the annular body is absorbed by the spacer, and the tightening margin of the spacer with respect to the annular body is kept almost constant. Therefore, the load applied to the annular body is effectively transmitted to the mating member via the spacer.

In particular, if the coefficient of linear expansion of the part of the spacer in contact with the mating member is set to be approximately equal to that of the mating member, and the coefficient of linear expansion of the part of the spacer in contact with the annular body is set to a value approximately equal to that of the annular body, temperature changes There is no fluctuation in the fitting state of the spacer to the annular body throughout the front and rear directions, and a constant interference can be reliably maintained.

The mating surface of the annular body with the mating member is in a hard fitted state at the latest during operation of the annular body, and the load applied to the annular body and the maximum stress due to this fitting and temperature change are within the range of the material of the annular body. If the dimensions of the mating surface are set to be smaller than the maximum allowable stress, the load applied to the annular body will be shared by the annular body and the spacer and transmitted to the mating member, and the annular body will It will not break due to the applied load.

In addition, if a tapered surface is formed on the axial end surface of the annular body and an intermediate spacer having an opposite end surface with the same taper angle is interposed between the spacer and the spacer, the applied load will be applied to the spacer and the spacer. It is possible to share the role between the intermediate spacer, or between the annular body, the spacer, and the intermediate spacer.

In addition, if the angle of the tapered surface formed on the axial end face of the annular body is set to have a predetermined relationship with the axial length and diameter at the center of the thickness of the annular body, the annular shape may change due to temperature changes. It is possible to prevent the effects of thermal stress on the body.

〔Example] Embodiments of the present invention will be described below based on the drawings.

FIG. 1 shows an embodiment in which the present invention is applied to the assembly of an inner ring (annular body) and a support (a mating member) of a cylindrical roller bearing.

The cylindrical roller bearing shown in the figure has an inner ring 20, a foreign import 30, and an inner ring 2.
It is comprised of cylindrical rollers 50 held and guided by a cage 51 between the outer ring 30 and the outer ring 30.

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

Each spacer 40 has an annular portion 40a that fits on the outer peripheral surface of the shaft 10.
and a cylindrical portion 40b that projects in the axial direction from the annular portion 40a and fits into the outer circumferential side fitting surface 23 of the end of the inner @ 20, and the inner circumferential surface 42 of the annular portion 40a is connected to the shaft 10. The inner circumferential surface 43 of the cylindrical portion 40b is tightly engaged with the inner ring 20 by tight fitting, or by adhesion, welding, screw fastening, etc.
It is fitted against the

The opposite end surfaces 22 of the inner ring 20 and the opposing end surfaces of the spacer 40 are not limited to being in contact with each other, but may be opposed with an appropriate axial clearance therebetween.

The constituent material of the inner ring 20 of the above-mentioned cylindrical roller bearing is 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 of the inner ring 20 is
It is smaller than the linear expansion coefficient α5 of the case 10. The constituent material of the outer ring 30 is bearing steel.

Further, the spacer 40 has an inner circumferential portion fitted to the shaft 10 and an outer circumferential portion fitted to the inner ring 20 . It is made of a material whose linear expansion coefficient in the radial direction changes in the same direction as the change in the radial direction due to the linear expansion coefficient α5 of the shaft 10 and the linear expansion coefficient α of the inner ring 20.

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

When constructing the spacer/10 using each of the above-mentioned materials, the linear expansion coefficient of the inner circumferential portion including the inner circumferential surface 42 of the annular portion 40a of the spacer 40 is approximately equal to the linear expansion coefficient α5 of the shaft 10. The linear expansion coefficient of the outer circumferential portion including the inner circumferential surface 43 of the cylindrical portion 40b of the spacer 40 is set approximately equal to the linear expansion coefficient α of the inner ring 20, and extends from the inner circumferential portion to the outer circumferential portion. It is preferable to set the linear expansion coefficient of the intermediate portion to change continuously or stepwise and to decrease sequentially.

Next, the shaft 10 when the temperature T during use of the cylindrical roller bearing configured as described above becomes higher than the temperature T8 during installation. The load transmission mechanism between the inner ring 20 and the spacer 40 will be explained.

Now, when installing the bearing, it is assumed that the inner ring 20 and the shaft 10 are loosely fitted, the spacer 40 is tightly fitted to the shaft 10 and the inner ring 200, and the shaft 10 is made of steel (linear expansion coefficient αs), The inner ring 20 is made of a ceramic material (linear expansion coefficient αj), the spacer 40 is made of a composite material or a laminated material, and the shaft 10
The linear expansion coefficient α of the inner circumferential side portion in contact with is approximately equal to the linear expansion coefficient α5 of the shaft 10, and the linear expansion coefficient α of the outer circumferential side portion in contact with the inner ring 20. is approximately equal to the linear expansion coefficient α of the inner ring 20.

When the bearing is installed, the fitting clearance between the inner ring 20 and the shaft 10 is Δd1, the interference between the spacer 40 and the shaft 10 is Δδ2, the interference between the spacer 40 and the inner ring 20 is △D, then when the bearing is used, For example, the fitting clearance of the inner ring 20 with respect to the shaft lO is Δd−(α5−αj)(Tb−T,)d, and the fitting clearance of the spacer 40 with respect to the shaft 10 is Δδ+(α
5-αh, ) (Tb Ta) d, and the interference of the spacer 40 with respect to the inner ring 20 is calculated as ΔD+(α4-αko)(T,-Ta)D.

The amount of change in the fitting clearance and interference is influenced by the relationship between them, but the amount of change in the fitting clearance of the inner ring 20 with respect to the shaft 10 (α, α, ) (Tb-Ta)
If d is set to be smaller than the clearance Δd during installation, even if the fitting clearance of the inner ring 20 with respect to the shaft 10 changes, this will cause the spacer 40 to
It can be considered that the interference for 0 and inner@20 is hardly affected.

Then, the amount of change in the interference of the spacer 40 with respect to the shaft 10 (α5−αb+)(Tb T−)d is α5−αa, so it is a value close to zero, and the inner ring of the spacer 40 20
(α, αk.) (Tb
T-) Similarly for D, α, -α,. Therefore, since these values are close to zero, the interferences Δd and ΔD when the spacer 40 is attached to the shaft 10 and the inner ring 20 can be maintained almost constant before and after the temperature change even if the temperature rises during use. It will be dripping.

In reality, the amount of change in the interference (or gap) described above influences each other, but since the linear expansion coefficient of the spacer 40 is configured to have directionality as described above, the temperature varies from Ta to T
, the linear expansion coefficient α of the spacer is adjusted so that the total change in the fitting distance of the fitting surfaces 42 and 43 due to the change in , becomes close to zero.
, and the degree of change in the radial direction, it is possible to keep the interference ΔD substantially constant.

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

In the above embodiment, the inner ring 20 is tightly fitted to the shaft 10 both when the bearing is installed and when it is in use.
Depending on the difference in coefficient of linear expansion between the shaft 10 and the shaft 10, the shaft 10 may be configured to be tightly fitted with a tightening margin at the latest during use. In this case, the maximum tensile stress σ1.8X on the inner peripheral side fitting surface 21 of the inner ring 20, that is, the shaft 1
The sum of the maximum tensile stress due to the interference with 0, the maximum tensile stress due to the load applied to the bearing, and the compressive stress due to the interference on the outer circumferential side fitting surface 23 of the inner ring 20 is
is smaller than the allowable tensile stress σ1 of the constituent material, and the maximum compressive stress σC on the outer peripheral side fitting surface 23 of the inner ring 20
m++x, that is, the sum of 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 tensile stress due to the interference on the inner peripheral side fitting surface 21 of the inner ring 20 is , allowable compressive stress σ of the constituent material of the inner ring 20. Each fitting surface 21 of the inner ring 20 is made smaller than the
, 23 are preferably set.

With such a configuration, when the temperature T during use of the bearing rises higher than the temperature Ta during installation, the interference of the spacer 40 with respect to the inner ring 20 becomes equal to the interference of the spacer 40 with respect to the shaft 10. Although it will be affected by the interference of the inner ring 20 with respect to the shaft 10, since the coefficient of linear expansion 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 will be affected. Amount of change in white (α5α
kl) (Tb - Ta) d and the shaft 1 of the inner ring 20
The sum of the amount of change in the interference of the spacer 40 with respect to the shaft 10 that occurs as the interference is made relative to 0 is absorbed by the internal strain of the spacer 40 and becomes a value close to zero.

For this reason, the inner ring 20 of the spacer 40 set when installing the bearing
The interference ΔD with respect to the axis 10 is the interference Δδ with respect to the axis 10
Even if the temperature changes, it will remain almost constant throughout the period before and after the temperature change.

As a result, the load applied to the bearing is divided into a portion that is transmitted to the shaft 10 via the spacer 40 and a portion that is transmitted directly to the shaft 10 through the inner fitting surface 21 of the inner ring 20.
Compared to the case of the above embodiment in which the load is transmitted through the spacer 40, the load shared by the inner ring 20 through the spacer 40 is reduced, so the maximum permissible load of the bearing is increased by that amount. Or, the allowable tensile stress σ7 and allowable compressive stress σ of the inner ring 20. The total transmittable load can be maximized by setting the load transmitted by each fitting surface 2 and 23 to an optimum value according to the value of .

Moreover, even if the bearing load is shared on the inner ring 20, the inner ring 20
Each mating surface 2 is adjusted such that the maximum tensile stress and maximum compressive stress of 0 are smaller than each allowable maximum stress of its configuration + J material.
Since the dimension is set to 1.23, the inner ring 20 will not be destroyed.

In this circumferential roller bearing, the end surface of the axial end portion 41 of the cylindrical portion 40b of the spacer 40 closely opposes the end surface of the cylindrical roller 50, and also functions as a guide collar for the cylindrical roller 5o. The outer diameter surface of the axial end portion 41 closely opposes the inner diameter surface of the retainer 51 and also serves as a guide ring for the retainer 51.

Only one of these functions may be used.

In the above embodiment, the linear expansion coefficient α of the inner peripheral side portion of the spacer 40 is
, is approximately equal to the linear expansion coefficient α5 of the shaft 10, and the linear expansion coefficient α of the outer circumference side portion. Although we have described a case in which the linear expansion coefficient α4 of the inner ring 20 is set approximately equal to The rate of change in the coefficient of linear expansion in the direction depends on the temperature difference between when the bearing is installed and when it is in use, the difference in the coefficient of linear expansion between the inner ring 20 and the shaft 10, the dimensional specifications, and the axis between the inner ring 20 and the spacer 40. It can be appropriately selected to have the optimum value and predetermined directionality depending on the installation conditions for 10G2, etc.

FIG. 2 shows an embodiment in which the present invention is applied to a four-piece assembly of an inner ring (annular body) and a shaft (a mating member) of a ball bearing. The ball bearing shown in the figure has an inner ring 20. Outer ring 30, inner ring 20 and outer ring 3
The inner peripheral side fitting surface 21 of the inner ring 20 is fitted to the shaft 10 with a clearance fit, and A pair of spacers 4 that tightly engage the shaft 10 are provided on the outer peripheral side fitting surface 23.
0 is fitted by interference fit. These axes 10
, regarding the constituent materials of the inner ring 20 and the spacer 40,
This is similar to the case of the cylindrical roller bearing shown in the figure.

In this embodiment, both end surfaces 22 of the inner ring 20 in the axial direction expand in diameter in the outward opening direction with respect to the central axis, and have a diameter of θ1 with respect to a cross section perpendicular to the axis. θ2 (formed on a tapered surface with an oblique angle,
A pair of intermediate spacers 45 having opposing surfaces having the same inclination angle as the end surfaces 22 are disposed between the inner ring 20 and the spacer 40 while being firmly engaged with the support 10. 20
It is sandwiched. This intermediate spacer 45 is made of a material having the same coefficient of linear expansion as the shaft 10.

In the ball bearing configured as described above, 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 by the spacer 40, which is
Since the load shared by the intermediate spacer 45 can be transmitted to the shaft 10 via the spacer 2, the load shared by the inner ring 20 is reduced compared to the case where the load is transmitted only by the spacer 40.

In this embodiment as well, the inner peripheral side fitting surface 21 of the inner ring 20 is in a tight fitting state with an interference with the shaft 10 at the latest when the bearing is in use, and the maximum tensile stress of the inner ring 20 and the maximum Each mating surface 21.23 may be dimensioned such that the compressive stress is less than the respective maximum allowable stress of its constituent materials. With this configuration, the load applied to the bearing can also be transmitted to the shaft 10 via the inner fitting surface 21 of the inner ring 20, so the spacer 40
The load shared by the inner ring 20 is further reduced compared to the case where the load is transmitted through the intermediate spacer 45 and the inner ring 20.

In addition, in this embodiment, both end surfaces 22 of the inner ring 20
The inclination angle θ1. If θ2 is set as below,
It is possible to prevent the influence of thermal stress generated on the contact surface between the inner ring 20 and the intermediate spacer 45 and the fitting surface between the inner ring 20 and the shaft 10 due to temperature changes between when the bearing is installed and when the bearing is used.

If the axial length of the inner ring 20 at the center of its wall thickness is Wll, and the diameter is L, then the axial length change of both end faces 22 due to temperature change ΔT is Xl+ΔX2, and the radial length change is V1. Δy2 is determined by the following formula.

The conditions under which there is no relative length change due to temperature change in the axial and radial directions of the inner ring 20 are given by the following equation.

Therefore, α5≠α1. Assuming ΔT≠0, θ8 of the above equation. θ2 is positive when both end surfaces of the inner ring 20 are tapered surfaces that expand in diameter in the direction of opening outward, as shown in the figure, and negative when, on the contrary, they are tapered surfaces that decrease in diameter in the direction of opening inward. .

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

In addition to the case shown in the figure, the installation of the intermediate spacer 45 can be done by firmly engaging the intermediate spacer 45 with the shaft 10, and then tightly fitting the spacer 40 onto the outer peripheral surface of the intermediate spacer 45. Alternatively, the intermediate spacer 45 and the spacer 40 may be joined and fixed together.

In each of the above embodiments, a case has been described in which an inner ring made of a ceramic material is attached to a shaft made of a steel material, but the present invention is not limited to such a case. The same can be applied to the case of mounting on a shaft made of a material such as an alloy.

Further, the present invention can be applied not only to a bearing in which the inner ring and the shaft have different linear expansion coefficients, but also to a bearing in which the outer ring and the axle box have different linear expansion coefficients.

In addition, the present invention also provides that the temperature during use of the bearing is
The present invention can be applied not only to cases where the temperature is higher than 1 o'clock, but also to cases where the temperature is lower during use than when the bearing is installed.

Furthermore, the present invention can be applied not only to rolling bearings, but also to cases where an annular body that is a component of a sliding bearing or other device is used as a mating member having a different coefficient of linear expansion.

〔Effect of the invention〕

As explained 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 transferred to the mating member through the spacer fitted to the annular body. Even if the engagement state of the spacer with the mating member or the fitting state of the annular body with the mating member changes due to the temperature difference between the time of installation and the time of use, the amount of these changes is absorbed by the internal strain of the spacer whose coefficient of linear expansion changes in the radial direction, and the interference of the spacer with respect to the annular body can be kept almost constant before and after the temperature change. Therefore, load transmission by the spacer is effectively performed as originally designed, and the upper limit of the transferable load can be easily increased.

Further, according to the present invention, the applied load is not transferred to the spacer, but to the fitting surface between the annular body and the mating member, or in addition to this, the intermediate member that clamps the tapered axial end face of the annular body. If the load capacity of the annular body is configured to be able to be transmitted also by a spacer, not only the load capacity of the annular body is further increased, but also by setting the angle of the Taper surface formed on the axial end face of the annular body to a predetermined angle, It also becomes possible to prevent concentration of thermal stress due to temperature changes.

Furthermore, according to the present invention, it is possible to reduce the fitting clearance between the annular body and the mating member, which not only facilitates centering during installation, but also maintains concentricity with the mating member during operation. Since it can be held with high precision, the high performance of the attached device is maintained and a highly reliable attachment device can be obtained.

[Brief explanation of drawings]

Fig. 1 is a vertical sectional side view of the upper half of an embodiment in which the present invention is applied to a cylindrical roller bearing, and Fig. 2 is a vertical sectional side view of the upper half of an embodiment in which the invention is applied to a ball bearing. , Figure 3 is
This is a vertical cross-sectional side view of the upper half of a conventional cylindrical roller bearing (not showing the state). In the figure, 10 is the shaft (mating member), 20 is the inner ring (annular body),
21 is the inner peripheral side fitting surface of the inner ring, 22 is the axial end surface of the inner ring,
23 is a fitting surface on the outer peripheral side of the inner ring, 40 is a spacer, 42 is a fitting surface of the spacer with respect to the shaft, /I 3 te1 is a fitting surface of the spacer with respect to the inner ring, and 45 is an intermediate spacer.

Claims (6)

[Claims] (1) The annular body fitted to the outer or inner circumference of the mating member has a linear expansion coefficient different from that of the mating member, and the annular body is fitted to the peripheral surface of the annular body on the opposite side of the mating surface with the mating member. A mounting device in which both end surfaces of an annular body in the axial direction are supported by a pair of spacers that firmly engage the outer periphery or the inner periphery of a mating member. Constructed of a material whose coefficient of linear expansion in the radial direction from 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 expansion in the radial direction between the mating member and the annular body. An annular body mounting device characterized by: (2) Claim (1) wherein the portion of the spacer in contact with the mating member has a coefficient of linear expansion approximately equal to that of the mating member, and the portion of the spacer in contact with the annular body has a coefficient of linear expansion approximately equal to that of the annular body. )
Attachment device for the annular body described. (3) The fitting surface of the annular body with respect to the mating member is in a firm fitting state at the latest during operation of the annular body, and the load applied to the annular body and the maximum stress due to this fitting and temperature change are The annular body attachment device according to claim 1 or 2, wherein the annular body attachment device has dimensions set to be smaller than the maximum allowable stress of the body's constituent material. (4) At least one end surface in the axial direction of the annular body is a tapered surface, and an intermediate spacer having an opposite end surface at the same angle as the tapered surface is sandwiched between the annular body and the spacer. 1) The annular body attachment device according to any one of (3). (5) The angles θ_1 and θ_2 with respect to the axis-perpendicular cross section of both end faces in the axial direction of the annular body are positive when they open outward with respect to the central axis, and negative when they open inward, and the axis at the center of the thickness of the annular body. The annular body mounting device according to claim 4, wherein the relationship between the direction length W_P and the diameter D_P is set as tanθ_1+tanθ_2=2W_P/D_P. (6) The annular body is a bearing ring of a rolling bearing, and the axial end of the spacer fitted to the bearing ring has at least one of the functions of a guide collar for the rolling elements and a guide ring for the cage. The annular body attachment device according to any one of claims (1) to (5), comprising: