WO2014010542A1

WO2014010542A1 - Roller bearing and method for use of same

Info

Publication number: WO2014010542A1
Application number: PCT/JP2013/068606
Authority: WO
Inventors: 河島　壯介
Original assignee: 株式会社空スペース
Priority date: 2012-07-10
Filing date: 2013-07-08
Publication date: 2014-01-16
Also published as: JP6106830B2; JP2014016005A

Abstract

Provided is a roller bearing equipped with a structure for preventing direct contact between rolling elements that are subjected to a load, or a structure for preventing indirect competition, through a partition wall intervening between rolling elements, between rolling elements that are subjected to a load, wherein a difference in the amount of thermal expansion between the inner and outer races due to a temperature differential is utilized to bring the bearing into a pre-compressed state during operation when the inner race reaches higher temperature than the outer race, and prevent premature damage due to skew of the rolling elements and the like. When at a stop, on the other hand, the bearing is brought into a non-precompressed state by virtue of the inner race and the outer race being at approximately the same temperature, facilitating assembly/disassembly operations thereof.

Description

Rolling bearing and method of using the same

The present invention relates to a rolling bearing used in a guide roll for continuous casting in an iron factory.

It has been common to use rolling bearings for applications such as guide rolls for continuous casting in steel mills without preloading. In these applications, severe disturbances such as mixing of water and foreign matter, high temperature, impact load, and the like act, so that the rolling bearing is required to be easily detached and attached on the premise of frequent disassembly and replacement. Since the fitting of the guide roll shaft and the inner ring is usually an interference fit, when the rolling bearing is in a preload state, the four parts of the shaft, the inner ring, the rolling element, and the outer ring are integrated in the axial direction. As a result, it was difficult to remove the bearing from the guide roll shaft without damaging the raceway surface and rolling elements, which was the main reason for using it without a preload.
In addition, in the conventional rolling bearing, the operation of the individual rolling elements becomes unstable due to the disturbance as described above, and competition with other rolling elements occurs via the cage, but the rolling elements receiving preload have a competing force. Since it could not be escaped, there was a possibility of premature bearing damage.

However, a no-load region is likely to occur in a rolling bearing in a no-preload state, and the rolling element loses its rotating force in the no-load region, which may cause damage such as skidding and peeling. In addition, when the roller is a rolling element, the restriction from the inner and outer rings is released in the no-load region, causing a phenomenon (skew) in which the rotating shaft of the roller is twisted, and the maximum load compared to when preload is applied. Incorporating disadvantages such as an increase in the contact pressure of the rolling element.
These problems may occur even when used in vacuum, high temperature, underwater, etc. where the lubrication environment is poor, in addition to the use of guide rolls for continuous casting of steel.

The inventor of the present application previously increased the ratio of rotation to the revolution of the rolling element in that region by changing the radius of rotation of the rolling element to be small for a part of the bearing race, and increased the revolution speed of the rolling element that escaped from the region. A mechanism has been invented in which the rolling elements are accelerated by raising them so that the rolling elements receiving a load do not contact each other. See

Patent Documents

1 and 2.
According to this mechanism, the problem of competing in the preload state is eliminated, so that early damage to the bearing can be prevented, and at the same time, the problem due to the no preload state can be solved. From now on, this technology will be referred to as “Autonomous Decentralized Rolling Bearing”, the product name of the applicant, Sora Space.

JP2007-177993A JP2007-192412

However, even if it is possible to operate in a preload state with a configuration such as an autonomous decentralized rolling bearing, it is difficult to assemble / disassemble the bearing and guide roll shaft without damaging the raceway surface and rolling elements. It was. SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a rolling bearing having a function of bringing the rolling elements that receive loads during operation into non-contact with each other so as to be in a preload state during operation and to be in a non-preload state during stoppage. is there. Here, the preload state refers to a state in which a majority of the rolling elements receive a positive contact pressure from the inner ring raceway and the outer ring raceway in a state where no external load is applied.

An inner ring having an inner ring raceway on an outer peripheral surface, an outer ring having an outer ring raceway on an inner peripheral surface, and a plurality of rolling elements interposed between the inner ring raceway and the outer ring raceway, In a rolling bearing comprising a mechanism for preventing direct contact or a mechanism for preventing rolling elements from competing indirectly through a partition wall interposed between the rolling elements under load, the inner ring temperature is higher than the outer ring temperature. It is characterized in that it is in a preload state when the temperature is high, and is in a non-preload state when the temperatures of the inner ring and the outer ring are substantially the same or when the inner ring temperature is lower than the outer ring temperature.

As a mechanism to prevent direct contact between rolling elements under load, it has a configuration of "autonomous distributed rolling bearing" that makes the rolling elements non-contact by changing the revolution and rotation ratio during the operation of the rolling elements It is characterized by that.
In addition, as a mechanism to prevent the rolling elements from competing indirectly through a partition wall interposed between the rolling elements that receive the load, the rolling element is interposed between the rolling elements and changes its rolling element transfer direction dimension due to temperature change. It is characterized by comprising a rolling element partition wall comprising a shape memory alloy or a bimetal.

Further, the method of using the rolling bearing includes: an inner ring having an inner ring raceway on at least an outer peripheral surface; an outer ring having an outer ring raceway on an inner peripheral surface; and a plurality of rolling elements interposed between the inner ring raceway and the outer ring raceway. A method of using a rolling bearing having a mechanism configured to prevent the rolling elements from contacting each other directly or indirectly via a partition wall between the rolling elements, and the inner and outer rings of the bearing designed separately In a state where the inner ring is exposed to a temperature higher than the outer ring above the lower limit temperature difference, a majority of the rolling elements receive a positive contact pressure from the inner ring raceway and the outer ring raceway, and the inner ring and the outer ring have substantially the same temperature. It is characterized in that the positive contact pressure is released in a state.

According to the present invention, a rolling mechanism is provided that has a mechanism that prevents direct contact between rolling elements that receive a load, or a mechanism that prevents rolling elements from competing indirectly through a partition interposed between the rolling elements that receive a load. When the bearing is operated in an environment where the inner ring temperature is higher than the outer ring temperature, it is in a preload state, which improves the problems caused by the no-preload state as described above, as well as during bearing assembly and maintenance. At the time of bearing replacement, since the temperature difference between the inner and outer rings is zero because the operation is stopped, a non-preload state with good workability can be achieved.

Rolling bearing with aligning ring according to the present invention Cylindrical roller bearing according to the present invention Deep groove ball bearing according to the present invention Spherical roller bearing according to the present invention

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

Fig. 1 shows a rolling bearing with a centering ring for a guide roll for continuous casting in a steel factory. (A) is an XX sectional view of (B), (B) is a YY sectional view of (A), and (C) is a ZZ sectional view of (A). An outer ring 1 having an outer ring raceway 1a on the inner side, an inner ring 2 having an inner ring raceway 2a on the outer side, and a plurality of cylindrical rollers 3 inserted between these transfer grooves so as to be able to roll, Has a step 3a having a slightly smaller diameter than the outer diameter. Further, flanges 1e are provided on both end faces of the outer ring, and collars 2b are provided on both end faces of the inner ring, so that the cylindrical rollers 3 are prevented from falling off and the axial positions of the inner and outer rings are constrained so that a slight relative displacement is possible.

The deceleration bar 4 is fitted into an annular groove 1b on both sides of the outer ring raceway 1a, and both ends thereof are freely restricted by pins 5 driven into the outer ring. The end surface on the inner ring side of the speed reduction bar 4 abuts on the step 3a of the cylindrical roller, and the opposite end surface has a gap with respect to the bottom of the groove 1b. Therefore, the roller 3 is configured to be pressed against the inner ring raceway 2 a by a weak force due to the bending elasticity of the speed reduction bar 4. On the outer ring raceway, an outer ring raceway nib 1c having a surface cut by about 10 μm from the other part (ZZ cross section position) is formed in the central portion (YY cross section position) of the speed reduction bar 4. The configuration so far is a typical configuration of an autonomously distributed rolling bearing.

The outer ring 1 has an outer diameter surface formed on a spherical surface with the shaft center of the bearing as the center of rotation. The outer ring 1 is aligned with the aligning ring 6 that is slidably fitted to this surface. It is composed. The inner ring of this bearing is fitted to both shaft ends of a guide roll shaft for continuous casting (not shown in the figure) of an iron factory, and the outer ring is fixed to a bearing box (not shown in the figure). When the semi-solid cast steel passes through the pair of guide rolls, the bearing inner ring is heated from the cast steel and receives an upward load F shown in FIG.
The overall structure of the guide roll and the bearing not shown in this figure is the same as that disclosed in FIG. 1 of Japanese Patent Application Laid-Open No. 2010-1921, for example.

The operation of the autonomous distributed rolling bearing will be briefly described. At the position shown in FIG. 1C, the outer diameter surface of the cylindrical roller 3 supports the rolling load on the inner ring raceway 2a and the outer ring raceway 1a as in the case of a normal rolling bearing. However, at the position shown in FIG. 1B, the outer diameter surface of the cylindrical roller 3 does not contact the outer ring raceway 1c, and the step portion 3a of the cylindrical roller rolls on the inner ring side end surface of the speed reduction bar 4. At this time, since the radius of rotation of the cylindrical roller 3 decreases from R1 to Ra, the rotational speed of the cylindrical roller 3 increases and at the same time the revolution speed decreases. When the cylindrical roller escapes from the area (B), it returns to the original speed, that is, the revolution speed increases as the rotation speed decreases, so that a gap 3b is formed between the cylindrical roller and the subsequent cylindrical roller. When the interval between the inner ring raceway 2a and the outer ring raceway 1a of this bearing is slightly smaller than the outer diameter of the roller 3, that is, when preload is applied, all the cylindrical rollers 3 other than the position in FIG. The gap 3b is maintained without falling due to its own weight.

On the other hand, since the revolution speed of the roller 3 at the position shown in FIG. 1 (B) is decreased, the roller 3 contacts the subsequent cylindrical roller 3 at the contact point 3c. However, since the roller 3 is not preloaded by the outer ring raceway 1c and is only pressed against the inner ring raceway 2a by a weak force due to the bending elasticity of the speed reduction bar 4, the contact pressure at the contact point 3c is small and its adverse effect. Is limited.
Even if no special outer ring raceway 1c is provided, by making the preload equal to the upper load F, the outer diameter surface of the roller 3 at the position shown in FIG. It is also possible to have a contact state that hardly receives.
As described above, this embodiment constitutes an “autonomous distributed rolling bearing” in which the rolling elements are brought into non-contact with each other by changing the revolution and rotation ratio during the operation of the rolling elements. For further details, refer to the prior art documents.

Based on the above configuration, the internal clearance of the rolling bearing is as follows. When the temperature of the outer ring 1 and the inner ring 2 is substantially the same, there is an internal gap. When the continuous casting equipment is in operation, for example, the inner ring of the bearing in which heat from the high-temperature cast steel is transferred via the guide roll is approximately less than the outer ring. It becomes 30 ℃ high temperature.
As a result, during operation, the amount of thermal expansion of the inner ring is greater than that of the outer ring, so that a majority of the cylindrical rollers 3 are in a preload state in which positive contact pressure is received from the track of the inner and outer rings (with no external load applied). Here, the majority means that the cylindrical roller at the position of FIG. 1 (b) is not preloaded by the outer ring raceway 1c, and that there are a small number of cylindrical rollers that are not subjected to contact pressure due to variations in product dimensions. However, it is more preferable that 3/4 or more of the rollers are in a preload state.

This example has a configuration of an autonomous decentralized rolling bearing in which the rolling elements are in non-contact by changing the revolution and rotation ratio during the operation of the rolling elements, so that there is no competition that tends to be a problem in the preload state, and Since most of the rollers are preloaded, problems such as roller skew can be suppressed.
On the other hand, it is difficult to remove the preloaded bearing from the guide roll shaft during maintenance or the like. (In general, since the fit between the shaft and the inner ring is an interference fit, the parts from the shaft to the bearing outer ring cannot be moved in the axial direction in the preload state, and the raceway surface and the rolling element are easily damaged.) When the temperatures of the outer ring 1 and the inner ring 2 are substantially the same, there is an internal gap, so that the inner ring integrated with the shaft can be removed by removing the collar 1e of the outer ring and removing the roller 3.

FIG. 2 shows a second embodiment, a cylindrical roller bearing. A cylindrical roller 3 which is a plurality of rolling elements interposed between the outer ring raceway 1a of the outer ring 1 and the inner ring raceway 2a of the inner ring 2, and a rolling element partition wall which is interposed between the rolling elements to prevent contact between the rolling elements. A cage 7 serving as a role is provided. The cage 7 has a U-shaped partition wall 7a extending in the axial direction of the bearing between the cylindrical rollers 3 (the number is equal to the number of cylindrical rollers), and each partition wall portion 7a is disposed on both outer sides in the axial direction of the cylindrical roller. The partition wall 7a is made of a shape memory alloy or bimetal. For lubrication, low temperature grease is filled to 10% or less of the bearing space volume.

With the above configuration, the internal clearance of the rolling bearing and the amount of play in the circumferential direction of the cylindrical roller 3 change as follows.
When the temperatures of the outer ring 1 and the inner ring 2 are both the same at −50 ° C., the bearing has an internal gap and the end of the U-shaped partition wall 7a of the cage 7 is open (solid line 7c in the figure). ). The amount of play in the circumferential direction of each cylindrical roller 3 at that time is restricted to a narrow area where the open ends 7c of the partition walls on both sides do not interfere, and the cylindrical rollers 3 are evenly distributed.

From this state, when the device (for example, a refrigeration compressor) supported by the rotation of the bearing is started and the inner ring temperature rises and the difference from the outer ring temperature becomes 8 ° C., the cylindrical roller 3 is heated by the thermal expansion of the inner ring raceway diameter. The majority of the cylinders are in a preload state that receives positive contact pressure from the inner and outer ring raceways, and the change in ambient temperature (increase in inner ring temperature and sliding frictional heat with rolling elements) causes the U-shaped section of the cage to The partition wall 7 a changes to a closed end (broken line 7 d in the figure) and creates a gap between the partition wall 7 a and the cylindrical roller 3.

In this state, the cage can freely rotate until it comes into contact with the outer diameter surface of any one of the cylindrical rollers 3, but since it is in a preload state, at least one side of the closed end portion 7d of the U-shaped cross section of the cage. Does not come into contact with the cylindrical roller 3, and the competition between the cylindrical rollers via the cage does not occur. In other words, the rolling elements are prevented from indirectly competing with each other via a partition wall interposed between the rolling elements receiving the load. Conventionally, a bearing provided with a preload used in such a poorly lubricated environment is likely to have a problem in which rolling elements compete with each other via a cage, but this embodiment improves this.

Further, when the bearing is replaced, the temperature of the inner and outer rings of the bearing rises to room temperature, and the inner and outer rings are at substantially the same temperature.
Even in the preload state, it is conceivable that the arrangement of the rollers is disturbed as the operation time elapses and the rolling elements compete with each other indirectly via the partition wall 7a. However, if the operation is intermittent, no preload is applied during the stoppage. At the same time, the end of the U-shaped partition wall 7a of the cage 7 is opened, so that the cylindrical rollers 3 are evenly redistributed.

In addition, the grease filling amount of a normal bearing is about 50% of the bearing space volume, but in this embodiment, the rolling elements are prevented from competing with each other. The heat transfer between them is reduced and the thermal resistance of the bearing is increased. As a result, a temperature difference between the inner and outer rings can be secured, and a reliable preload state during operation can be created. Similarly, it is also effective to use a rolling element or an outer ring as a ceramic for the purpose of obtaining a high thermal resistance. Further, shape memory alloy or bimetal may be used for the ring 7b instead of the partition wall 7a of the cage, or both may be made of the material. This is because the play of the cylindrical roller in the circumferential direction can be changed also by expanding the diameter of the annular portion.

FIG. 3 shows a third embodiment, a deep groove ball bearing. The role of a rolling element partition wall that is interposed between the rolling elements and prevents the rolling elements from contacting each other, and balls 8 that are a plurality of rolling elements interposed between the outer ring raceway 1a of the outer ring 1 and the inner ring raceway 2a of the inner ring 2. It has a spacer 9 that fulfills The spacer 9 is formed by inserting a coil 9b made of a shape memory alloy into the hollow portion of the collar 9a, and there are the same number of balls between the balls 8.

When the outer ring 1 and the inner ring 2 are at the same temperature, for example, 20 ° C. or less, the bearing is in a non-preloaded state having an internal gap, and the shape memory alloy coil 9b is extended (FIG. 3A), Each ball is evenly distributed by elastically expanding the space between the balls.
Next, when the temperature of the inner ring rises, a majority of the balls 8 are in a preload state that receives positive contact pressure from the raceway of the inner and outer rings, and changes in ambient temperature (rising of the inner ring temperature and sliding frictional heat between the balls 8 and the coil 9b The coil 9b contracts. At the same time, each spacer is tilted by gravity or centrifugal force, for example, the state shown in FIG. 3 (b). However, with respect to variations in the ball spacing due to the difference in the revolution speed of each ball, the spacer is tilted with a slight force. Since the correction is made, it is a mechanism that prevents the rolling elements from competing indirectly through the partition wall interposed between the rolling elements that receive the load, and the problem of competing does not occur.
In addition, this example assumes operation | movement in a high vacuum, and coats the coil and collar of a spacer with a solid lubricant, without using fats and oils. A vacuum environment and the use of a solid lubricant are advantageous conditions for making a bearing with high heat resistance.

FIG. 4 shows a guide roll bearing for continuous casting in a steel factory in which the structure of an autonomous distributed rolling bearing similar to that of the first embodiment is incorporated in the fourth embodiment, a self-aligning roller bearing.
(A) is a cross section parallel to the shaft center at the center position of the speed reduction bar, and, practically, a cross section on the opposite side to the phase of the outer ring that receives the maximum load (generally, the phase of the outer ring that minimizes the load in the bearing). (B) is a view in the X direction of the speed reduction bar 4. A plurality of spherical rollers 10 interposed between the outer ring raceway 1a of the outer ring 1 and the inner ring raceway 2a of the inner ring 2 are arranged in two rows, and the center of curvature of the outer ring raceway is set to one point to constitute a centering bearing. .

Both ends of the spherical roller 10 have round groove-shaped step portions 10a that are slightly smaller in diameter than the outer diameter, and these round grooves are outside the speed reduction bar 4 fixed by inserting both ends into the speed reduction bar fixing hole 1f of the outer ring 1. It matches the diameter, and the spherical roller 10 is held down with a weak force. The spherical roller 10 is displaced in the left-right direction in FIG. 5A by the aligning operation, but the speed reduction bar 4 is easily bent in a direction parallel to the axis of the spherical roller 10, and the stepped portion 10a is detached from the speed reduction bar by this round groove. It prevents that. The outer ring raceway 1a forms an outer ring raceway portion 1c whose surface is shaved at a position near the center of the speed reduction bar 4 shown in FIG. 4A. This portion does not contact the outer diameter surface of the spherical roller 10, but the outer ring The outer ring raceway other than the raceway portion 1 c comes into contact with the outer diameter surface of the spherical roller 10.

The guide roll shaft of the continuous casting facility needs to maintain a predetermined temperature in order to maintain the quality of the material to be manufactured. This embodiment assumes a case in which the inner ring temperature during steady operation is approximately 120 ° C. or higher as a bearing that rotatably supports a continuous casting guide roll shaft.
On the other hand, when the outer ring of the bearing is as hot as the inner ring, the bearing box that supports the outer ring and the frame that fixes the bearing box are metal integrated by fastening bolts etc. Since these are overwhelmingly large in surface area as compared with bearings, the ambient temperature is raised. However, since the periphery needs to be a temperature at which an operator can enter, enormous cooling energy is required.

In this example, focusing on the fact that the contact point between the rolling element and the raceway surface of the inner and outer rings is the smallest among the members from the guide roll shaft to the bearing outer ring, Yes. More specifically, the configuration in which the rolling elements in the load region are not in contact with each other reduces the grease that reduces the thermal resistance to 10% or less with respect to the bearing space volume. Similarly, the space volume of the bearing is increased without using a metal rolling element partition wall (such as a cage) that lowers the thermal resistance. Further, the shape of the spherical roller 10 is set such that diameter> length, and the thermal resistance is increased.

With this configuration, the inner / outer ring temperature difference can be made 50 ° C. or higher, that is, the outer ring temperature at the inner ring temperature 120 ° C. can be made 70 ° C. or less. Therefore, it is possible to greatly reduce the amount of heat dissipated from the bearing housing and the gantry, and the contact pressure between the raceway and the rolling element caused by the difference in the thermal expansion of the inner and outer rings at that time (the preload not including the external force due to the roll work) ) Is estimated to be 1.5 GPa or more. Although this is a very high value as a preload of conventional common sense, it is a result of reducing the bearing width by making the shape of the spherical roller 10 diameter> length so as to increase the thermal resistance of the bearing.

In order to avoid fatal damage to the bearing even when the inner ring temperature rises above the set due to abnormalities in peripheral devices and the temperature difference between the inner and outer rings is more than twice the lower temperature difference between the inner and outer rings, It is effective to make the contact pressure of 4 GPa or less. Specifically, it can be achieved by appropriately designing the material (thermal expansion coefficient) and thickness of the outer ring and the bearing box.
Further, since the alignment mechanism of this figure is not a requirement of the present invention, it can be applied to a cylindrical roller bearing, a needle bearing, or a tapered roller bearing without an alignment mechanism.

Conventionally, the temperature difference between the inner and outer rings of a bearing is often managed to be less than 8 ° C. with 0 ° C. being the ideal, and there has been no precedent for using a rolling bearing with an intentional temperature difference. This is due to the occurrence of strong sliding friction such as competing with changes in preload, heat generation caused by sliding friction, and the large amount of lubricant necessary to alleviate these problems, so that the temperature difference between the inner and outer rings is not in a specific range. Because it was difficult to manage. Therefore, the method of using a rolling bearing with an intentional temperature difference according to the present invention can be used in combination with a configuration that substantially reduces sliding friction generated inside a general rolling bearing.
Further, in order to use the bearing in a better state, heating means or cooling means for controlling the temperature difference between the inner and outer rings can be provided in the inner ring and / or the outer ring of the bearing.

Although the embodiments have been described above, the present invention can be applied to a very wide range, and thus the configuration is changed for each embodiment. However, the present invention is not limited to this. For example, the “autonomous distributed rolling bearing” of the first embodiment or the fourth embodiment may be replaced with the cage of the second embodiment or the spacer of the third embodiment, or vice versa. Similarly, types of rolling elements (cylindrical rollers, needles, balls, spherical rollers, tapered rollers) and types of lubrication (grease, oil air, gel, solid lubrication), bearing surface treatments and types of materials applied to each embodiment (Chrome steel, ceramics, silicon alloy, etc.) may be selected individually, and does not limit the scope of application of the present invention. For example, the present invention can be applied to all the rolling bearings of the embodiments described in two patent documents which are prior art documents.
In addition to the continuous casting guide roll, the usage environment is also suitable for an environment in which the inner ring of the bearing becomes hotter than the outer ring during operation, for example, for supporting impellers such as steam and gas turbines.

It can be widely used for rolling bearings used in steel continuous casting machine rolls and equipment using rolling bearings.

1a outer ring raceway 1c outer ring raceway 2a inner ring raceway 3 cylindrical roller 4 deceleration bar 7 cage 8 ball 9 spacer

Claims

An inner ring having an inner ring raceway on an outer peripheral surface, an outer ring having an outer ring raceway on an inner peripheral surface, and a plurality of rolling elements interposed between the inner ring raceway and the outer ring raceway, In a rolling bearing comprising a mechanism for preventing direct contact or a mechanism for preventing rolling elements from competing indirectly through a partition wall interposed between the rolling elements subjected to a load, the temperature of the inner ring is the temperature of the outer ring. The rolling bearing is characterized in that it is in a preload state when the temperature is higher than that, and the temperature of the inner ring and the outer ring is substantially the same, or when the temperature of the inner ring is lower than the temperature of the outer ring, there is no preload state.
The rolling bearing according to claim 1, comprising a structure of “autonomous distributed rolling bearing” as a mechanism for preventing direct contact between the rolling elements receiving the load.
As a mechanism to prevent the rolling elements from competing indirectly through a partition wall interposed between the rolling elements that receive the load, the rolling element is interposed between the rolling elements and changes its rolling element transfer direction dimension due to temperature change. The rolling bearing according to claim 1, further comprising a rolling element partition wall comprising a shape memory alloy or a bimetal.
When the temperature of the inner ring is 30 ° C. or more higher than the temperature of the outer ring, the maximum value of the positive contact pressure received by the majority of the rolling elements from the inner ring raceway and the outer ring raceway is 1.5 GPa or more. The rolling bearing according to claim 1, wherein
The inner ring includes at least an inner ring raceway on the outer peripheral surface, an outer ring having an outer ring raceway on the inner peripheral surface, and a plurality of rolling elements interposed between the inner ring raceway and the outer ring raceway. Or a method of using a rolling bearing having a mechanism for preventing contact indirectly through a partition wall between rolling elements, wherein the inner ring exceeds the lower limit temperature difference between inner and outer rings of a separately designed bearing. In a state exposed to higher temperatures, a majority of the rolling elements receive a positive contact pressure from the inner ring raceway and the outer ring raceway, and the positive contact pressure is released when the inner ring and the outer ring are at substantially the same temperature. A method of using the rolling bearing, wherein the rolling bearing is used.
The method of using a rolling bearing according to claim 5, wherein a filling amount of grease or lubricating oil with respect to the bearing space volume during steady operation is 10% or less.
6. The method of using a rolling bearing according to claim 5, wherein a heating means or a cooling means for controlling a temperature difference between the inner and outer rings is provided on the inner ring and / or the outer ring of the bearing.
The method for using a rolling bearing according to claim 5, wherein the inner ring temperature during steady operation is 120 ° C. or higher.
The method for using a rolling bearing according to claim 5, wherein the inner and outer ring lower limit temperature difference is 8 ° C. or more.
6. The rolling device according to claim 5, wherein, during steady operation, the rolling element is a bearing box in which a majority of the rolling elements have a maximum positive contact pressure received from the inner ring raceway and the outer ring raceway of 4 GPa or less. How to use the bearing.