JPS639720A - Gap correcting device for rolling bearing - Google Patents

Abstract

PURPOSE:To correct a bearing gap due to a temperature change, and prevent a reduction in bearing performance, by installing a spacer formed of a shape memory alloy having a two-direction characteristic at high and low temperatures between an end surface of a loosely fitted race of a bearing and a side surface of a positioning member opposed to the race. CONSTITUTION:A spacer 60 is installed between a back surface of an outer race 31 of a tapered roller bearing 30 and a side surface of an outer race retainer 11 as a positioning member opposed to the outer race 31. The spacer 60 is formed of a shape memory alloy having a two-direction operating characteristic wherein the spacer 60 becomes an annular member 60a at low temperatures and becomes a disc spring member 60b at high temperature, such a deformation being reversible. Three of the spacer 60 at low temperatures are stacked in such a manner that the direction of deformation is counter to each other. Accordingly, at high temperatures, as the outer race 31 loosely fitted with a housing 10 is pressed by the high-temperature operation of the spacer, the axial expansion of the housing 10 is maintained at an initially set quantity, thus preventing a reduction in bearing performance.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a clearance correction device for a rolling bearing, and in particular, the present invention relates to a clearance correction device for a rolling bearing, and in particular, it uses a shape memory alloy to compensate for changes in the axial clearance or preload due to the influence of temperature during use of the rolling bearing. This is corrected using a spacer.

[Conventional technology]

Generally, rolling bearings have an outer ring attached to a housing.
The inner ring is attached to the shaft and used, but depending on the type of machine or device to which the bearing is assembled, a bearing molded on the housing side is used.

An example of this type of bearing is shown in FIG. The figure shows a housing 10 made of aluminum alloy material and a shaft 20 made of steel material.
A combination type bearing in which two single-row tapered roller bearings 30 and 40 are mounted face-to-face between the
The outer ring 31.41 of the tapered roller bearing 30°40 is the stationary side bearing ring attached to the housing 10 with a loose fit, and the inner ring 32.42 is the rotating side bearing ring attached to the shaft 20 with a tight fit. It is a bearing ring. Tapered rollers 33.43 with a retainer 34.44 are interposed between the raceway surfaces of the outer ring 31.44 and the inner ring 32.42.

The outer ring 31.41 is attached to the outer ring retainer 11.41 whose back surface (small diameter side end surface) is fixed to both axial end surfaces of the housing 10.
The inner rings 32.42 are positioned by the inner rings 31.42, whose opposing back surfaces (end faces on the guide collar side) abut against the inner ring spacer 21 fitted on the shaft 20 to regulate the axial distance between them, and the inner rings 32.42 are positioned by the outer rings 31.42. 41 and inner ring 32.42 and tapered roller 34.4
4, a certain set axial clearance is provided.

A belt pulley 50 is fixed to one end of the shaft 20 by a napht 51, and is rotatably driven by an endless belt (not shown) that is passed around the belt pulley 50.

[Problem that the invention seeks to solve]

As mentioned above, in a rolling bearing that is installed in combination with an aluminum alloy housing and a steel shaft, the housing's net expansion coefficient is larger than the shaft's linear expansion coefficient, so the temperature increases while the bearing is in use. As it rises, the axial displacement (elongation) of the housing becomes larger than the axial displacement of the shaft, and the distance between the bearings on the housing side becomes larger than the corresponding shaft length L2, so L , and L2 becomes larger than the axial clearance set when the bearing is installed, there will be play between the outer ring and the inner ring.

This kind of play between the inner and outer rings can cause vibrations, abnormal wear, and other deterioration in bearing performance, so as a measure to prevent this, bearings are sometimes installed using only one raceway (the outer race in the case of the bearing in Figure 13). Means for applying a preload such as strongly tightening with a tensioner or pressing with a spring are used.

However, some machines and devices in which bearings are assembled are undesirable to be preloaded because they need to be used at low torque. Therefore, such bearings have to endure the play that occurs between the inner and outer rings due to the rise in temperature, resulting in a problem that the bearing performance deteriorates and the bearing life is shortened.

The present invention solves the above problems and adjusts the excessive or insufficient axial clearance caused by temperature changes during use of the bearing to an appropriate clearance without applying preload or other means. The purpose of the present invention is to provide a gap correction device that can.

[Means for solving problems]

The clearance correction device of the present invention provides for at least two rolling bearings installed in combination between a housing and a shaft having different coefficients of linear expansion. A spacer made of a bidirectional shape memory alloy is incorporated between one end surface of the loosely fitting bearing ring and the side surface of the positioning portion opposite to the end surface of the bearing ring.

This spacer memorizes the amount of displacement corresponding to the positive or negative axial clearance that exceeds the set amount that occurs due to temperature changes during use of the bearing, and operates reversibly on the high temperature side and the low temperature side, respectively. It has the characteristics of

[Effect]

In the spacer in the clearance correction device of the present invention, when the linear expansion coefficients of the molding materials of the housing and the shaft are different, whether the axial clearance that exceeds the set amount caused by the temperature rise is positive with respect to the set amount; Depending on whether the value is negative or not, the operation is as follows.

(1) When a positive axial clearance that exceeds the set amount occurs due to temperature rise, the spacer increases its axial width by the amount of displacement equivalent to the axial clearance that exceeds the set amount.
The bearing ring on the loosely fitted side is moved in the direction to reduce the axial clearance, and when the temperature drops, the axial width of the spacer shrinks and returns to its original shape, returning the bearing ring to its original position. This compensates for changes in the axial clearance that occur due to temperature changes.

(2) When a negative axial clearance that exceeds the set amount occurs due to temperature rise, the spacer reduces the axial width by the amount of displacement equivalent to the axial clearance that exceeds the set amount, and the fit is loose. By moving the side bearing ring in the direction of increasing the axial clearance, and when the temperature drops, the axial width of the spacer increases and returns to its original shape, and the bearing ring is returned to its original position. Corrects changes in axial clearance that occur due to temperature changes.

〔Example〕

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a longitudinal cross-sectional side view showing a first embodiment of the present invention, and FIG. 2 is an enlarged view of its main parts, both of which show the mounting of the bearing.

This embodiment is an application of the present invention to the tapered roller bearing shown in FIG. 13 described above, and there is no difference in structure in terms of the molding materials for the housing and shaft, the components of the tapered roller bearing itself, and their mounting. Therefore, the same parts will be designated by the same reference numerals, and repeated explanation will be omitted.

A spacer 60 is incorporated between the back surface of the outer ring 31 of the bearing 30 mounted on the left side of the two tapered roller bearings 30 and 40 and the side surface of the outer ring holder (positioning part) 11 opposing this. In this state, a predetermined axial clearance is provided.

This spacer 60 is formed from a shape memory alloy having bidirectional operating characteristics, and the shape on the low temperature side is an annular body 60a as shown in FIG. The disc spring-like bodies 60b as shown in (b) have a characteristic of alternately and reversibly fluctuating, and three pieces on the low temperature side are stacked so that the deformation directions are opposite to each other. It is assembled.

The deformation operation temperatures on the high temperature side and low temperature side of each spacer 60 are set at temperatures divided into three stages from room temperature to the maximum temperature during use of the bearing, and are set in a stepwise manner. or lower) temperatures.

In addition, the amount of displacement (increase/decrease in axial width) h2-hl of the combined three spacers 60 due to temperature change is the positive axial displacement amount (increase/decrease in axial width) h2-hl that occurs in excess of the set amount when the maximum temperature is reached during use of the bearing. The amount is set to correspond to the gap in the direction, and the respective annular bodies 60a and disc spring-like bodies 60b are sequentially displaced at different operating temperatures.

When the temperature rises during use of the bearing configured as described above, the axial elongation of the housing IO becomes larger than the axial elongation of the shaft 20, so the outer ring 31 of the bearing 30 becomes larger axially outward than the inner ring 32. The displacement causes a positive axial clearance that exceeds the set amount, but each time the temperature rises to a predetermined temperature, each annular body 60a of the spacer 60 recovers its shape on the high temperature side due to its shape memory property and sequentially changes its axis. Increase direction width.

Therefore, each time the axial width of each annular body 60a of the spacer 60 increases, the outer ring 31 attached to the housing 10 with a loose fit is pressed by the spacer 60 and moves inward in the axial direction. Correct the axial clearance stepwise to make it equal to the set amount.

Furthermore, when the temperature during use of the bearing changes from high to low, each spring-like body 60b of the spacer 60 returns to its low-temperature shape due to its shape memory property and sequentially changes its axial width. The outer ring 31 is moved axially outward and returned to its original position for assembly.

FIG. 3 is a longitudinal sectional side view showing the main parts of a second embodiment of the invention.

In this embodiment, the present invention is applied to the case where the inner ring 32 is attached to the shaft 20 with a loose fit in the bearing shown in FIG. ) 21, a spacer 60 made of an alloy having bidirectional shape memory characteristics is incorporated.

In this embodiment as well, when the temperature rises, the axially outward displacement of the outer ring 31 becomes larger than that of the inner ring 32, creating a positive axial clearance that exceeds the set amount, but the spacer 6
As each annular body 60a of 0 gradually recovers its shape on the high temperature side and increases its axial width as the temperature rises, the inner ring 3
2 is moved outward in the axial direction, the increased axial clearance is corrected stepwise and becomes equal to the set amount.

When the temperature drops from the high temperature state, each spring-like body 60b of the spacer 60 sequentially returns to the low temperature side shape and reduces its axial width, and the inner ring 32 moves axially inward to complete the assembly. The attachment returns to its original position.

FIG. 5 illustrates the relationship between the axial clearance and the displacement amount of the spacer with respect to temperature change in the first and second embodiments described above.

As shown in the figure, the spacer is displaced at every predetermined temperature, and the axial clearance is corrected stepwise.

By configuring as in the first and second embodiments above, there is no play between the inner and outer rings, which prevents vibrations, abnormal wear, etc. that would occur in conventional bearings of this type without preload. The cause of performance deterioration will be removed.

FIG. 6 is a longitudinal side view showing the third embodiment of the present invention, and FIG.
The figures are enlarged views of the main parts, and both figures show the bearings in their original state.

In this embodiment as well, the housing 10 is made of aluminum alloy material, and the shaft 20 is made of steel. However, the structure of mounting the bearings is different from that of the first and second embodiments, and two single-row bearings are used. The tapered roller bearings 30, 40 are mounted with their backs facing each other.

In these bearings 30, 40, the outer ring 31.41 is connected to the housing 1.
The stationary side bearing ring is attached to the shaft 20 with a loose fit, and the inner ring 32.42 is the rotating side bearing ring attached to the shaft 20 with a firm fit. Note that 33.43 indicates a tapered roller, and 34.44 indicates a cage.
' Of the two tapered roller bearings 30 and 40 mentioned above, there is a space between the back surface of the outer ring 31 of the bearing 30 installed on the left side and the side surface of the stepped portion (positioning portion) 13 of the housing 10 facing thereto. A spacer 60 is incorporated, and the inner ring 32
The back surface of the shaft 20 is positioned in contact with the side surface of the shoulder portion 22 of the shaft 20, and in this state, a predetermined axial clearance is provided. The outer ring 41 of the bearing 40 mounted on the right side has its front surface in contact with the side surface of the stepped portion 14 of the housing 10, and the inner ring 42 has a nut 2 screwed onto the shaft 20 from the rough surface.
3 is tightened and positioned.

The spacer 60 of this embodiment is made of an alloy having bidirectional shape memory characteristics on the high temperature side and the low temperature side, as in the previous embodiment, but the shape on the low temperature side is the same as that of the fourth embodiment.
The disc spring-like body 60b as shown in FIG. thing 3
The pieces are assembled in series with their deformation directions opposite to each other.

The deformation operation temperatures on the high-temperature side and the low-temperature side of each spacer 60 are set to temperatures divided into three stages from room temperature to the maximum temperature during use of the bearing, and the temperature increases stepwise ( or lower) temperatures.

In addition, the amount of displacement (increase/decrease in axial width 1) h, -h of the combined three spacers 60 due to temperature change is the negative value that occurs when the maximum temperature is reached during use of the bearing, which exceeds the set amount. The disk spring-like body 60b and the annular body 60a are set to have an amount equivalent to the axial clearance of , and the disc spring-like body 60b and the annular body 60a are sequentially displaced at different operating temperatures.

When the temperature rises during use of the bearing configured as described above, the axial elongation of the housing 10 becomes greater than the axial elongation of the shaft 20, so the outer ring 31 of the bearing 30 is displaced more axially outward than the inner ring 32. As a result, the state is the same as if an excessive preload was applied, and a negative axial clearance exceeding the set amount occurs, but each spring-like body 60b of the spacer 60 changes its shape each time the temperature rises to a predetermined temperature Due to the memory property, the shape on the high temperature side is recovered and its axial width is gradually reduced. Therefore, the outer ring 31 attached to the housing 10 in a loose fit
Every time the axial width of > is reduced, the axial width is moved inward in the axial direction by a length corresponding to the reduced width, and the reduced axial clearance is corrected stepwise to make it equal to the set amount.

Furthermore, when the temperature during use of the bearing changes from a high temperature to a low temperature, each annular body 60a of the spacer 60 returns to the shape on the low temperature side each time the temperature decreases to a predetermined temperature due to its shape memory property, and sequentially changes its axial width. The outer ring 31 is pressed by the spacer 60 and moves axially outward, returning to the original position at the time of assembly.

FIG. 8 is a longitudinal sectional side view showing the main parts of a fourth embodiment of the present invention.

In this embodiment, the present invention is applied to the case where the inner ring 32 is attached to the shaft 31 in a loose fit in the bearing shown in FIG.
A spacer 60 made of an alloy having bidirectional shape memory characteristics is incorporated between the shoulder portion (positioning portion) 22 and the side surface thereof.

In this embodiment as well, when the temperature rises, the displacement of the outer ring 31 toward the outside in the axial direction becomes larger than that of the inner ring 32, creating a negative axial clearance that exceeds the set amount.
Each time the spring-like body 60b of each spring 60b gradually recovers its high-temperature side shape as the temperature rises and reduces its axial width, the inner ring 32 moves axially outward, so the reduced axial clearance is corrected stepwise to become equal to the set amount.

When the temperature drops from the high temperature state, each annular body 60a of the spacer 60 sequentially returns to its low temperature shape and increases its axial width, and the inner ring 32 is pressed axially inward and assembled. The attachment returns to its original position.

FIG. 9 illustrates the relationship between the axial clearance when the temperature rises and the preload load (displacement load) due to the displacement of the spacer caused by the decrease in the axial clearance in the third and fourth embodiments described above. It is.

In the figure, the two-dot chain line indicates the displacement load when a disc spring is used as a spacer instead of the spacer of the present invention.

As is clear from the figure, when a disc spring is used, the preload increases as the temperature rises, but by using the spacer of the present invention, the preload increases as the temperature rises to a predetermined level. It can be seen that the preload is released.

By adopting the configurations as in the third and fourth embodiments described above, excessive preload is not applied, so there are problems such as increased torque, overheating, seizure, and grease deterioration in conventional bearings of this type. This eliminates the causes of deterioration in bearing performance.

Regarding the number of spacers to be incorporated in each of the first to fourth embodiments, depending on the axial clearance caused by temperature change, by combining several types of spacers with different deformation operation temperatures, it is possible to follow the axial clearance. Although it is possible to perform a near-correction with good performance, only one may be incorporated depending on the usage conditions of the bearing.

Further, in each of the above embodiments, a case was described in which a spacer was incorporated into the back surface of the bearing ring of the loosely fitted bearing on one side of two tapered roller bearings installed in combination. Regarding the bearing on the other side,
It is also possible to adopt a configuration in which spacers are incorporated in corresponding positions similar to those described above.

FIGS. 10 and 11 are perspective views showing other embodiments of the spacer of the present invention, respectively.

The spacer 61 in FIG. 10 has a shape on the low temperature side as shown in the figure (a).
), the shape of the high temperature side is an arc-shaped curved body 61b as shown in the same figure (bl), or on the contrary, the shape of the low temperature side is the arc shape of the figure (b) The curved surface body 6lb, the high temperature side is the plate-like plane body 61a in the same figure (al
In the former case, it is used as a spacer for the bearings of the first and second embodiments, and in the latter case, it is used as a spacer for the bearings of the third and fourth embodiments.

When assembling this spacer to the bearings of the first and second embodiments, as shown in FIG. The bearing of the first embodiment is a regular polygon inscribed in a circle with a diameter D (inner diameter DI of the housing 10). In the case of the second embodiment, the bearings are combined into a regular polygonal shape circumscribing a circle with a diameter d (the outer diameter dυ of the shaft 20. In FIG. 12, as an example, the case is combined into a regular octagonal shape. It is illustrated.

The amount of displacement of the combined spacers is the arc-shaped curved surface body 61
The sum t2 of the center vertical path of b and the plate thickness, and the plate thickness 1 of the plate-like plane body 61a. Difference with 1. -1. obtained as.

In addition, when assembling this spacer to the bearings of the third and fourth embodiments, a curved body 6 of equal length whose low temperature side is an arc shape is used.
1b is used, and arranged so that either the convex side or the concave side of each circular arc surface is on the same side and on the same plane, and in the case of the bearing of the third embodiment, the diameter D (housing In the case of the bearing of the fourth embodiment, the diameter d (outer diameter d of the shaft 20
Combine them into a regular polygon that circumscribes the circle of z).

The amount of displacement of the combined spacers is determined by the thickness of the plate-shaped plane body 61a, 1. , and the sum t: of the center longitudinal path of the arc-shaped curved surface body 61b and the plate thickness, 1°-1, and t is obtained.

These spacers may be combined into a regular polygon by using only spacers with the same amount of displacement tt tI, but by using multiple types of spacers with different curvatures of the arc-shaped curved surface bodies 51b and different operating temperatures, spacers of the same type may be combined. It is preferable to arrange and combine them on opposite sides of a regular polygon diameter. By using such a combination, the axial clearance caused by temperature change can be corrected in a stepwise manner, and the clearance correction can be performed with good followability.

The spacer 61 in FIG. 11 has a shape on the low temperature side as shown in FIG. 11(a).
A hollow body 62a with an elliptical cross section as shown in FIG. The high temperature side of the hollow body 62b is that of the hollow body 62a with an elliptical cross section shown in FIG. Each is used as a spacer for the bearing of the fourth embodiment.

When assembling this spacer to the bearing, the spacer of FIG. 10 is combined into a regular polygon as explained in FIG. 12.

In the bearings of the first and second embodiments, a plurality of hollow bodies 62a of equal length each having an elliptical cross section on the low-temperature side are used, and the central axis planes in the longitudinal direction including the major axis of each ellipse are arranged on the same plane. The bearing of the first embodiment is combined into a regular polygon inscribed in a circle with a diameter D (inner diameter D+ of the housing 10), and the bearing of the second embodiment is combined with a diameter d (outer diameter a+ of the shaft 20). ) into a regular polygon that circumscribes the circle.

The amount of displacement of the combined spacers is the circular cross-section hollow body 6
It is obtained as the difference δ2-61 between the outer diameter δ2 of the hollow body 2b and the outer diameter δ1 in the minor axis direction of the elliptical cross-section hollow body 62a.

Furthermore, in the bearings of the third and fourth embodiments, a plurality of hollow bodies 62b of equal length each having a circular cross section on the low temperature side are used.
Arranged so that the longitudinal center axis plane including the major axis of the elliptical cross section during each deformation operation is on the same plane,
In the case of the bearing of the third embodiment, the fourth
In the case of the bearings of the embodiment, they are combined into a regular polygon shape circumscribing a circle with a diameter d (outer diameter dz of the shaft 20).

Similarly to the above, the displacement amount of the combined spacers is obtained as the difference δ1-62 between the outer diameter δ of the elliptical cross-section hollow body 62a in the short axis direction and the outer diameter δ2 of the circular cross-section hollow body 62b.

In the case of the spacers of this embodiment as well, not only spacers having the same displacement amount δ2−δ are used to combine them into a regular polygon, but also the outer diameter δ in the short axis direction of the elliptical cross-section hollow body 62a and the operating temperature It is also possible to use a plurality of types with different values and combine the same types by arranging them on opposite sides of a regular polygon so that they are displaced stepwise for each operating temperature.

In each of the above-mentioned embodiments, the case where the bearing is attached to the device' is explained where the coefficient of linear expansion of the molding material for the housing is larger than that of the shaft. The present invention can also be applied to a bearing installed in a device where the linear expansion coefficient of the housing molding material is smaller than that of the shaft.
In the case of the bearings of the first and second embodiments, a negative axial clearance exceeding the set amount is generated due to temperature change.
For example, a configuration may be adopted that incorporates a disk spring-like spacer as shown in FIG. Since a gap is generated, for example, a configuration may be adopted in which the annular spacer shown in FIG. Become.

Furthermore, the present invention is not limited to the tapered roller bearing described in the above embodiments, but can also be applied to other rolling bearings, such as deep groove ball bearings, angular contact ball bearings, and guide collars on at least one of the outer ring and the inner ring. The cylindrical roller bearing can also have the same configuration as described above.

〔Effect of the invention〕

As explained above, the clearance correction device of the present invention is arranged so that at least one of the combined rolling bearings installed in the device where the linear expansion coefficients of the housing and the shaft are different is on the side where at least one bearing is loosely fitted. Between the bearing ring and the positioning part,
A configuration in which a spacer made of a shape memory alloy with bidirectional operating characteristics is incorporated, and the axial width of the spacer is displaced in response to temperature changes during bearing use, so that the axial clearance is corrected to be equal to the set amount. It is said that Therefore, according to the present invention, it is possible to adjust the change in the axial clearance due to temperature change when mounting the bearing without taking any measures such as applying preload. Since the phenomenon of preload loading is eliminated, causes of deterioration of bearing performance such as vibration, abnormal wear, overheating, and seizure are eliminated, making it the most suitable clearance correction device for bearings in machines and equipment that require low torque. It can be used as

[Brief explanation of the drawing]

FIG. 1 is a longitudinal cross-sectional side view showing a first embodiment of the present invention, and a second embodiment of the present invention is shown in FIG.
The figure is an enlarged view of the main part, FIG. 3 is a longitudinal sectional side view showing the main part of the second embodiment of the invention, and FIG. 4 is a longitudinal sectional view of the spacer. Figure (bl is the shape on the high temperature side, Figure 5 is a chart showing the relationship between the axial clearance and the amount of displacement of the spacer due to temperature change, Figure 6 is the third figure of this invention)
A vertical side view showing the embodiment, FIG. 7 is an enlarged view of the main part,
FIG. 8 is a vertical side view showing the main part of the fourth embodiment of the present invention, FIG. 9 is a chart showing the relationship between the axial clearance due to temperature change and the spacer displacement load, and FIG. FIG. 11 is a perspective view showing an example; the figure (al indicates the low temperature side, in the figure) is the shape of the high temperature side; FIG. 11 is a perspective view showing still another example of the spacer; 12 is a front view showing a state in which a spacer is combined, and FIG. 13 is a vertical side view showing an example of a conventional combination type tapered roller bearing. be. In the figure, 10 is a housing 11, 12 is an outer ring holder, and 13.
14 is a stepped portion of the housing, 2o is a shaft, 21 is an inner ring spacer,
22 is the shoulder of the shaft, 30.40 is the tapered roller bearing, 31
．． 41 is an outer ring, 32.42 is an inner ring, and 60 is a spacer. Figure 4 (a) (b) Figure 5 1 Figure 9 Figure 10 = Figure 11 Figure 12 Figure 13

Claims (17)

[Claims] (1) In a rolling bearing in which at least two bearings are installed between a housing and a shaft having different coefficients of linear expansion, one end face of the bearing ring on the loosely fitting side of at least one bearing; The amount of displacement corresponding to the axial clearance that exceeds the set amount that occurs due to temperature changes between the end surface side of the bearing ring and the side surface of the positioning part that is opposite to the side surface of the bearing ring is memorized, and the displacement is reversible between the high-temperature side and the low-temperature side. A clearance correction device for a rolling bearing, which is characterized by incorporating a spacer made of a bidirectional shape memory alloy that operates as follows. (2) A bearing in which the coefficient of linear expansion of the housing is larger than that of the shaft, and the bearing ring on the housing side is loosely fitted,
2. A clearance correction device for a rolling bearing according to claim 1, wherein a spacer having an axial width on a high-temperature side that is larger than an axial width on a low-temperature side is incorporated in an axially outer end surface of the bearing ring. (3) A bearing in which the coefficient of linear expansion of the housing is larger than that of the shaft, the bearing ring on the shaft side is loosely fitted, and the spacer has an axial width on the high temperature side that is larger than the axial width on the low temperature side.
The clearance correction device for a rolling bearing according to claim 1, which is incorporated in an axially inner end surface side of the bearing ring. (4) A clearance correction device for a rolling bearing according to claim 2 or 3, wherein the shape of the spacer on the low temperature side is an annular body, and the shape on the high temperature side is a disc spring-like body. (5) A clearance correction device for a rolling bearing according to claim 4, wherein a plurality of types of spacers having different deformation operating temperatures are stacked on top of each other with deformation directions opposite to each other. (6) A plurality of spacers whose shape on the low temperature side is a plate-like flat body and whose shape on the high temperature side is an arcuate curved body are combined into a polygonal shape on the same plane with the same deformation direction. A clearance correction device for a rolling bearing according to claim 2 or 3. (7) The rolling bearing according to claim 6, wherein spacers of the same type among a plurality of types of spacers having different curvatures and operating temperatures of the arcuate curved surface are arranged on opposite sides of a regular polygon. Gap correction device. (8) A plurality of spacers whose shape on the low temperature side is a hollow body with an elliptical cross section and whose shape on the high temperature side is a hollow body with a circular cross section,
4. A clearance correction device for a rolling bearing according to claim 2 or 3, wherein the elliptical cross-sectional hollow bodies are combined into a polygonal shape so that the longitudinal center axis planes including the major axis lie on the same plane. (9) Claim 8, wherein spacers of the same type among a plurality of types of spacers having different outer diameters in the short axis direction of the elliptical cross-sectional hollow body and different operating temperatures are arranged on opposite sides of the regular polygon. Clearance correction device for rolling bearings as described in . (10) A bearing in which the coefficient of linear expansion of the housing is larger than that of the shaft, the bearing ring on the housing side is loosely fitted, and the axial width of the spacer on the high temperature side is smaller than the axial width on the low temperature side, The clearance correction device for a rolling bearing according to claim 1, which is incorporated in an axially inner end surface side of the bearing ring. (11) A bearing in which the coefficient of linear expansion of the housing is larger than that of the shaft, the bearing ring on the shaft side is loosely fitted, and the axial width of the spacer on the high temperature side is smaller than the axial width on the low temperature side, A clearance correction device for a rolling bearing according to claim 1, which is incorporated on the axially outer end surface side of the bearing ring. (12) Claim 10, wherein the shape of the spacer on the low temperature side is a disc spring-like body, and the shape on the high temperature side is a toric body.
A clearance correction device for a rolling bearing as described in item 1 or item 11. (13) A clearance correction device for a rolling bearing according to claim 12, wherein a plurality of types of spacers having different deformation operation temperatures are stacked on top of each other with deformation directions opposite to each other. (14) A plurality of spacers whose shape on the low-temperature side is an arcuate curved body and whose shape on the high-temperature side is a plate-like flat body are combined into a polygonal shape on the same plane with the same deformation direction. A clearance correction device for a rolling bearing according to claim 10 or 11. (15) The axial bearing according to claim 14, wherein spacers of the same type among a plurality of types of spacers having different curvatures and operating temperatures of the arcuate curved surface are arranged on opposite sides of the regular polygon. Gap correction device. (16) A plurality of spacers whose low-temperature side shape is a circular cross-section hollow body and whose high-temperature side shape is an elliptical cross-section hollow body are arranged so that the longitudinal central axis plane including the major axis of the elliptical cross-section hollow body A clearance correction device for a rolling bearing according to claim 10 or 11, wherein the devices are combined in a polygonal shape on the same plane. (17) Claim 16, wherein spacers of the same type are arranged on opposite sides of a regular polygon among a plurality of types of spacers having different outer diameters in the short axis direction of the elliptical cross-sectional hollow body and operating temperatures. Clearance correction device for rolling bearings as described in .