JP4748076B2 - Rolling bearing device - Google Patents

Description

  The present invention relates to a rolling bearing device that is used by applying a preload such as a tapered roller bearing or an angular ball bearing.

  Tapered roller bearings and angular contact ball bearings are used with axial preload applied. For example, in a gear-type drive transmission unit for an automobile such as a transmission unit, a tapered roller bearing is adopted at its main point (for example, a final reduction gear portion in the transmission unit). As shown in FIG. 6 (a), the tapered roller bearing 111 press-fits the rotating shaft 115 into the inner ring 133 and fits the outer ring 132 into the housing 125 of the transmission case, and then axially one side (arrow a A preload is given to). When the preload is applied in this manner, the outer ring 132 receives a component force on the inclined rolling surface of the tapered roller 134 and is displaced in the axial direction and the radial direction, and the left end surface 132 c and the outer peripheral surface 132 b are connected to the housing 125. The preload is supported by being pressed against the inner end face 125c and the inner peripheral face 125a.

On the other hand, in recent years, as a part of weight reduction, a transmission case is made of a light metal such as an Al alloy. Al has the highest linear expansion coefficient among structural materials (about 23.5 × 10 ⁻⁶ / ° C. at room temperature: hereinafter, the unit of linear expansion coefficient is abbreviated as ppm / ° C.) and constitutes a rotating shaft and a tapered roller bearing. There is a considerable difference from the linear expansion coefficient of steel (Fe-based material) (about 12 ppm / ° C. at room temperature).

When the rotating shaft and the housing are made of the same material, the dimensional change due to temperature is the same, so there is no significant change in the preload applied to the tapered roller bearing. However, if the housing is made of a light metal, the housing may change in size more than the rotating shaft due to temperature rise, and the preload may be lost.
Specifically, as shown in FIG. 6B, when the temperature of the transmission rises, the housing 125 and the rotating shaft 115 expand, and the inner circumferential raceway surface 132a of the outer ring 132 changes due to the difference in dimensional change due to the expansion. It moves away from the rolling surface of the tapered roller 134 in the direction of arrow b. That is, the axial gap and the radial gap between the outer ring 132 and the tapered roller 134 in the tapered roller bearing device 111 vary greatly depending on the temperature, resulting in insufficient preload. Such a shortage of preload causes gear rattle and causes noise.

As shown in FIG. 7, a tapered roller bearing device 140 in which a preload is applied to the outer ring 132 by a thrust washer 141 is disclosed as a means for solving such a problem. The basic structure of this tapered roller bearing device 140 is the same as in FIG. 6, and the same reference numerals are given to the same parts. Specifically, as shown in FIG. 7A, a thrust washer 141 is interposed between the housing 125 and the end of the outer ring 132. The thrust washer 141 has a flat shape at the time of cooling (at room temperature) (see FIG. 7A), and is elastically deformed into a taper shape larger than the width at the time of cooling when the temperature is raised to a certain temperature. (See FIG. 7 (b)) is formed from a shape memory alloy.
In this configuration, when the temperature is raised to a certain temperature, the outer ring 132 is urged inward in the axial direction (arrow e) by the action of the thrust washer 141 described above, and the axial gap and the radial gap between the outer ring 132 and the tapered roller 134 are reduced. It is possible to eliminate the preload shortage by suppressing the change.
Japanese Utility Model Publication No. 5-6250

  However, in the above-described prior art, the thrust washer 141 is not deformed into a tapered shape unless the temperature is raised to a certain temperature. Therefore, a sufficient preload is applied axially inward (arrow e) to the outer ring 132 until the temperature reaches the certain temperature. Could not grant. For this reason, there has been a problem that it is not possible to suppress gear rattle and noise generation until the temperature is raised to a certain temperature.

  The present invention has been made in view of such a situation, and it is possible to suppress the occurrence of insufficient preload due to thermal expansion in real time, and it is more effective to generate rattling and noise of the device. It is an object of the present invention to provide a rolling bearing device that can be prevented.

  A rolling bearing device according to the present invention includes a rolling element, and an outer ring having a raceway surface on the inner periphery that receives the rolling load and a radial load from the rolling element and a load directed to one side in the axial direction. The outer ring has a raceway surface on which the rolling element rolls, and an inner ring incorporated in the outer ring via the rolling element in a state where a preload is applied, and the outer ring surface of the outer ring are fitted together and the first line A housing having an expansion coefficient and an inner peripheral surface of the inner ring are fitted in a state in which relative movement in the axial direction and the circumferential direction is allowed, and an opposing surface that faces the end surface on the other axial side of the inner ring And having a second linear expansion coefficient smaller than the first linear expansion coefficient, at least one of an end surface on the other side in the axial direction of the inner ring and a surface facing the rotation shaft. Tapered groove extending in the circumferential direction and rollable in this tapered groove A pressing member introduced into the taper groove, and a biasing member that is introduced into the tapered groove and thermally expands as the temperature rises to bias the pressing member in the circumferential direction, and the inner ring and the rotating shaft The inner ring is pressed to one side in the axial direction by rolling the pressing member along the taper groove by relative movement in the circumferential direction with the biasing member, and accompanying thermal expansion of the housing Preload holding means for suppressing a decrease in the preload.

  According to the rolling bearing device configured as described above, when the housing is thermally expanded and the preload tends to be reduced, the biasing member is biased by the relative movement of the inner ring and the rotating shaft in the circumferential direction and the temperature rise. Due to the force, the pressing member can be rolled along the tapered groove, whereby the inner ring can be pressed toward one side in the axial direction to suppress the decrease in the preload in real time. In particular, since the pressing member can be urged in the circumferential direction by the urging member, the pressing member can be reliably rolled in the circumferential direction.

  The rolling bearing device according to the present invention includes an outer ring having a rolling element and a raceway surface on the inner circumference that receives the radial load from the rolling element and a load directed to one axial direction. And an outer ring having a raceway surface on which the rolling element rolls on the outer periphery and being preloaded, and an outer ring surface of the outer ring in the axial direction and the circumferential direction. A housing having a first linear expansion coefficient, a housing having a facing surface facing the end surface on one axial side of the outer ring, and an inner surface of the inner ring. Provided on at least one of a rotation shaft having a peripheral surface fitted therein and having a second linear expansion coefficient smaller than the first linear expansion coefficient, an end surface on one axial side of the outer ring, and an opposing surface of the housing A circumferentially extending tapered groove and the taper A pressing member introduced so as to be capable of rolling, and a biasing member that is introduced into the tapered groove and thermally expands as the temperature rises and biases the pressing member in the circumferential direction. By the relative movement of the outer ring and the housing in the circumferential direction and the urging by the urging member, the pressing member rolls along the taper groove, thereby pressing the outer ring toward the other side in the axial direction to heat the housing. Preload holding means for suppressing a decrease in the preload associated with expansion.

  According to the rolling bearing device configured as described above, when the housing is thermally expanded and the preload is about to decrease, the pressing is performed by the relative movement of the outer ring and the housing in the circumferential direction and the biasing by the biasing member. The member can be rolled along the taper groove, whereby the outer ring can be pressed toward the other side in the axial direction and the decrease in the preload due to the thermal expansion of the housing can be suppressed. In particular, since the pressing member can be urged in the circumferential direction by the urging member, the pressing member can be reliably rolled in the circumferential direction.

  In each of the rolling bearing devices described above, the biasing member is preferably made of a bimetal that biases the pressing member with a constant biasing force. In this case, the pressing member can be easily and reliably urged by the urging member.

  According to the rolling bearing device of the present invention, since it is possible to suppress a decrease in preload due to thermal expansion in real time, it is possible to more effectively prevent the device from rattling and noise due to insufficient preload. Can do.

Hereinafter, embodiments of the rolling bearing device of the present invention will be described with reference to the drawings.
FIG. 1 is a schematic sectional view showing a rolling bearing device 10 according to an embodiment of the present invention. The rolling bearing device 10 includes a transmission case 12, a gear box 13 incorporated in the case 12, and an input shaft 14 and an output shaft (rotating shaft) provided in parallel to each other so as to penetrate the gear box 13. 15. The input shaft 14 and the output shaft 15 are rotated in conjunction with a transmission gear 16 in the gear box 13.

  The transmission gear 16 is, for example, a manual type, and the input shaft 14 is provided with a plurality of input gears 18 having different numbers of teeth, and the output shaft 15 is provided with output gears 19 having different numbers of teeth. Shifting is possible by switching the combination of the meshing of the gear 18 on the input shaft 14 and the gear 19 on the output shaft 15 according to the speed ratio or the distinction between forward and reverse. As the input gear 18 and the output gear 19, a spur gear or a helical gear is used. The transmission gear 16 may be an automatic type using a planetary gear mechanism or the like.

  Both ends of the input shaft 14 are rotatably supported by cylindrical roller bearings 21 and ball bearings 22 fixed inside the case 12. Both ends of the output shaft 15 are supported by the first tapered roller bearing 11 and the second tapered roller bearing 23, respectively. The first tapered roller bearing 11 on one axial side (left side in FIG. 1) is fitted into a first housing 25 integral with the case 12, and the second tapered roller bearing 23 on the other axial side (right side in FIG. 1). Is fitted in a second housing 26 integral with the case 12.

  FIG. 2 is an enlarged cross-sectional view of a main part of the rolling bearing device 10 of the present invention. The first tapered roller bearing 11 includes an outer ring 32, an inner ring 33, and a plurality of tapered rollers (rolling elements) 34 disposed between the outer ring 32 and the inner ring 33. An outer peripheral surface 32b of the outer ring 32 is fitted to an inner peripheral surface 25a of the first housing 25, and an inner peripheral raceway surface 32a is formed on the inner peripheral surface of the outer ring 32. Yes. An outer peripheral raceway surface 33a on which the tapered roller 34 rolls obliquely is formed on the outer peripheral surface of the inner ring 33, and the inner peripheral surface of the inner ring 33 is allowed to move relative to the output shaft 15 in the axial direction and the circumferential direction. It is fitted in the state.

  Further, by fitting the output shaft 15 to the inner peripheral surface of the inner ring 33, a preload is applied to the outer ring 32 toward one side in the axial direction (arrow f). When the preload is applied in this way, the outer ring 32 receives a component force on the inclined rolling surface of the tapered roller 34 and is displaced in the axial direction and the radial direction, and the left end surface 32c and the outer peripheral surface 32b are the first housing. The preload is supported by being pressed against the inner end face 25c and the inner peripheral face 25a. Further, the large flange side end surface 33c of the inner ring 33 and the step surface 15a of the output shaft 15 face each other with a predetermined distance in the axial direction.

  The contact angle between the inner ring 33 and the tapered roller 34 and the contact angle between the tapered roller 34 and the outer ring 32 are increased from the other side in the axial direction (right side in FIG. 2) toward one side in the axial direction (left side in FIG. 2). Is set to Here, the contact angle conforms to the nominal contact angle defined in JIS B0104-1991.

The first housing 25 of the first tapered roller bearing 11 has a first linear expansion coefficient. On the other hand, the output shaft 15 has a second linear expansion coefficient smaller than the first linear expansion coefficient.
For example, in the first tapered roller bearing 11, the outer ring 32, the inner ring 33, and the rolling element 34 are all formed of steel (for example, bearing steel, case hardened steel, carburized steel), and the first housing 25 is a light metal. (Metal containing either Al or Mg as a main component (content of 10% by mass or more)), and the output shaft 15 is formed of steel (for example, carbon steel for mechanical structure). Preferably, the first housing 25 is made of Al or an Al alloy from the viewpoints of workability and corrosion resistance. As the Al alloy, for example, an Al alloy for die casting is used. In the present embodiment, the case 12 (see FIG. 1) is also made of an Al alloy, and the first housing 25 is integrated with the inner surface of the case 12.

  The linear expansion coefficient (first linear expansion coefficient) of Al that is the main component of the first housing 25 is 23 to 24 ppm / ° C., and the linear expansion coefficient of Fe that is the main component of the output shaft 15 and the first tapered roller bearing 11 ( The second coefficient of linear expansion) is about 12-13 ppm / ° C. In general, the bearing use environmental temperature in the automobile transmission is in the range of −40 ° C. or higher and 110 ° C. or lower (normally reached temperature excluding cold regions and high-speed continuous operation is 10 ° C. or higher and 80 ° C. or lower).

  FIG. 3 is an enlarged view of the large collar side end surface 33 c of the inner ring 33. 4 is a cross-sectional view taken along line AA of the inner ring in FIG. As shown in FIGS. 3 and 4, a preload holding means 40 is provided on the large collar side end surface (end surface on the other side in the axial direction) 33 c which is a surface facing the output shaft 15 in the inner ring 33. The preload holding means 40 is provided with a tapered groove 33b formed along the circumferential direction on the large end surface 33c, a pressing member 35 partially introduced into the tapered groove 33b, and a pressing member 35 as the temperature rises. A biasing member 36 is provided. The tapered groove 33b, the pressing member 35, and the urging member 36 are provided at least at three locations along the circumferential direction of the large collar side end surface 33c.

  Each of the tapered grooves 33b has a concave curved surface portion A whose depth gradually increases from the left edge of the circumferential direction toward the center of the bottom surface, and the same groove formed continuously from the center of the bottom surface to the right edge of the concave curved surface portion A. And a straight line portion B having a depth (see FIG. 4). The depth of the deepest portion (straight line portion B) of the tapered groove 33b is set to be equal to the radius of the pressing member 35. Moreover, the opening edge of the taper groove 33b is parallel from the right end edge to the center part and gradually becomes thinner from the center part toward the left end edge. Furthermore, the radial cross section of the taper groove 33b is set to a semicircular shape that matches the pressing member 35 (see FIG. 2).

  The urging member 36 is introduced into the tapered groove 33b with a part thereof protruding. The urging member 36 is made of a bimetal formed by joining a plate-like low expansion member and a high expansion member having different coefficients of thermal expansion, and has a substantially V-shaped cross section. The low expansion member is made of, for example, a low expansion material such as 36 to 46% Ni—Fe alloy. The high expansion member is, for example, Cu, Ni, 70% Cu—Zn alloy, 70% Ni—Cu alloy, 20% Ni—Mn—Fe alloy, Ni—Cr—Fe alloy, 20% Ni—Mo—Fe. It is made of a high expansion material such as an alloy or a 70% Mn—Ni—Cu alloy. The degree of expansion of the biasing member 36 can be changed by changing the metal composition of each of the low expansion member and the high expansion member to be joined. The urging member 36 gradually opens its legs due to thermal expansion accompanying a rise in temperature and urges the pressing member 35 with a constant urging force.

  The pressing member 35 is made of a steel ball and is made of the same material as the inner ring 33 (for example, bearing steel, case-hardened steel, carburized steel). For example, as shown in FIG. 3, when the inner ring 33 rotates in the direction of the arrow c and the temperature of the rolling bearing device 10 increases, the biasing member 36 expands in the left-right direction as the temperature increases. Thus, the pressing member 35 is urged in the circumferential direction by the urging member 36 and rolls on the bottom surface of the tapered groove 33b while being guided by the opening edge of the tapered groove 33b in the direction of arrow d. The diameter of the pressing member 35 is the same as the maximum width of the opening edge of the tapered groove 33b.

The pressing member 35 is sandwiched between the boundary portion between the concave curved surface portion A and the straight portion B, which is the central portion in the circumferential direction of the tapered groove 33b of the inner ring 33, and the step surface 15a of the output shaft 15. The biasing member 36 is biased in the circumferential direction indicated by the arrow d in FIG.
Further, the radius of curvature R of the concave curved surface portion A of the tapered groove 33b is such that the pressing member 35 urged by the urging member 36 rolls on its bottom surface and presses the inner ring 33 to one side in the axial direction. It is set to a value that can suppress a decrease in preload due to a difference in thermal expansion between the first housing 25 and the output shaft 15.

The operation of the rolling bearing device 10 according to the above embodiment will be described below.
When the temperature of the rolling bearing device 10 is maintained at a relatively low temperature, the difference in dimensional change due to thermal expansion of the first housing 25, the outer ring 32, and the output shaft 15 does not occur so much, and the preload is also kept constant. The relative movement between the output shaft 15 and the inner ring 33 is restricted by this preload.

When the rolling bearing device 10 is operated and the temperature rises, the linear expansion coefficients of the case 12 and the first and second housings 25 and 26 are larger than those of the output shaft 15, so that the first housing 25 expands greatly in the axial direction and the radial direction. However, the outer ring 32 tends to be separated from the tapered roller 34. That is, a decrease in preload is about to occur.
Then, relative movement in the circumferential direction between the inner ring 33 and the output shaft 15 is allowed, and the rotation resistance of the first tapered roller bearing 11 causes a rotation delay of the inner ring 33 with respect to the output shaft 15. That is, the inner ring 33 and the output shaft 15 are relatively moved in the circumferential direction. By the biasing of the biasing member 36 accompanying the relative movement and the temperature rise, the pressing member 35 rolls in the circumferential direction between the concave curved surface portion A of the tapered groove 33b and the stepped surface 15a of the output shaft 15 opposed thereto. . Thereby, the pressing member 35 further protrudes from the tapered groove 33b, and the inner ring 33 is pressed and moved to one side in the axial direction (left side in FIG. 2). The inner ring 33 moves to the one side in the axial direction to a position where the pressing force of the pressing member 35 and the reaction force from the first housing 25 are balanced, and the preload on the outer ring 32 is kept substantially constant. That is, the preload holding means 40 suppresses a decrease in preload accompanying the thermal expansion of the rolling bearing device 10 in real time.

  Further, when the temperature of the rolling bearing device 10 is further increased, the inner ring 33 and the output shaft 15 are further moved relative to each other, the urging member 36 is further thermally expanded and opened, and the pressing member 35 is further rolled in the circumferential direction. To do. Thereby, the inner ring 33 is further pressed and moved to the one side in the axial direction, and a decrease in the preload of the rolling bearing device 10 due to further thermal expansion is prevented.

In particular, in the rolling bearing device 10, since the pressing member 35 is urged in the circumferential direction by the urging member 36, the pressing member 35 can be reliably moved in the circumferential direction. Further, since the urging member 36 is made of bimetal, the pressing member 35 can be urged reliably and easily at a constant pressure. For this reason, the fall of the preload of a rolling bearing apparatus can be suppressed more reliably.
Furthermore, even when an impact load or the like is applied to the output shaft 15 in the direction opposite to the preload application direction (on the other side in the axial direction) due to shifting of the rolling bearing device 10 or connection / disconnection of a clutch (not shown), the preload is maintained. The means 40 moves the inner ring 33 to one side in the axial direction, so that the preload of the rolling bearing device 10 is appropriately maintained.

  Then, when the operation of the rolling bearing device 10 is stopped, the temperature of the first housing 25 decreases, the first housing 25 contracts, and the biasing member 36 closes, the inner ring 33 is interposed via the outer ring 32 and the tapered roller 34. Is moved to the other side in the axial direction. As a result, the pressing member 35 is pressed by the inner ring 33 and gradually rolls along the taper groove 33b in the opposite direction to that during the temperature rise, and finally returns to the center in the circumferential direction of the taper groove 33b.

  FIG. 5 is a schematic cross-sectional view showing a case where a rolling bearing device 10 according to another embodiment of the present invention is configured in a transmission. The basic structure of the rolling bearing device 10 is the same as that of the rolling bearing device 10 of FIG. 2, and the same reference numerals are given to the same portions. The rolling bearing device 10 according to this embodiment is different from the rolling bearing device 10 of FIG. 2 in that the inner peripheral surface of the inner ring 33 is press-fitted into the output shaft 15 and the relative movement between the inner ring 33 and the output shaft 15 is restricted. The outer peripheral surface 32b of the outer ring 32 is fitted to the first housing 25 in a state where relative movement in the axial direction and the circumferential direction is allowed, and the preload holding means 40 is connected to the outer ring 32 and the first ring. This is a point provided at a portion facing the housing 25.

  In this embodiment, the tapered groove 33 b of the preload holding means 40 is provided on the left end surface 32 c that is the surface of the outer ring 32 that faces the first housing 25. The tapered groove 33b has the same shape as the tapered groove 33b shown in FIGS.

Further, the left end surface 32c of the outer ring 32 and the inner end surface 25c of the first housing 25 are separated from each other by a predetermined distance. In this state, the pressing member 35 is connected to the concave curved surface portion A and the straight portion B of the tapered groove 33b of the outer ring 32. And the inner end face 25 c of the first housing 25.
Further, the radius of curvature R (see FIG. 4) of the concave curved surface portion A of the taper groove 33b is such that the pressing member 35 rolls on its bottom surface and presses the outer ring 32 toward the other side in the axial direction (arrow g). It is set to a value that can suppress a decrease in preload due to a difference in thermal expansion between the first housing 25 and the output shaft 15.

  In this embodiment, when the rolling bearing device 10 rises in temperature and the first housing 25 expands greatly in the axial direction and the radial direction, the outer ring 32 tends to move away from the tapered roller 34, that is, the preload decreases. Then, relative movement between the outer ring 32 and the first housing 25 is allowed, and the outer ring 32 rotates in the circumferential direction by the rotational torque of the output shaft 15 transmitted to the outer ring 32 via the inner ring 33 and the tapered roller 34. That is, the first housing 25 and the outer ring 32 are relatively moved in the circumferential direction. By the biasing of the biasing member 36 accompanying this relative movement and temperature rise, the pressing member 35 rolls on the concave curved surface portion A of the tapered groove 33b on the outer ring 32 side and the inner end surface 25c of the first housing 25, and the outer ring 32 is pressed and moved to the other side in the axial direction (right side in FIG. 5). The outer ring 32 moves to the other side in the axial direction to a position where the pressing force of the pressing member 35 and the reaction force from the output shaft 15 are balanced, and the preload on the inner ring 33 is kept substantially constant. That is, the preload holding means 40 suppresses a decrease in preload accompanying the thermal expansion of the rolling bearing device 10 in real time.

  Further, when the temperature of the rolling bearing device 10 is further increased, the outer ring 32 and the first housing 25 are further moved relative to each other, the urging member 36 is further thermally expanded and opened, and the pressing member 35 is further moved in the circumferential direction. Roll. Thereby, the pressing member 35 further rolls in the circumferential direction, and the outer ring 32 is further pressed and moved to the other side in the axial direction, thereby preventing a decrease in the preload of the rolling bearing device 10 due to further thermal expansion.

The present invention is not limited to the embodiment described above, and can be appropriately changed in design. For example, in the embodiment shown in FIG. 2, the taper groove 33b only needs to be provided on at least one of the large flange side end surface 33c of the inner ring 33 and the stepped surface 15a of the output shaft 15. In the embodiment shown in FIG. As long as it is provided on at least one of the left end surface 32 c of the outer ring 32 and the inner end surface 25 c of the first housing 25. Further, the urging member 36 may be composed of a rod-like or columnar member made of, for example, an Al alloy having a high coefficient of thermal expansion instead of the V-shaped member made of the bimetal. Further, the tapered groove 33b may be an inclined surface that is linearly inclined instead of the concave curved surface portion A described above. The pressing member 35 may be a tapered roller or a barrel-shaped rolling element in addition to the above-described sphere, and in this case, a tapered groove corresponding to the shape of the rolling element may be formed.
Although the rolling bearing device used in the transmission is shown in the above embodiment, the present invention can be applied to other devices such as a gear unit for a drive distribution shaft of a four-wheel drive vehicle. The rolling bearing is not limited to the tapered roller bearing, but may be another rolling bearing using preload such as an angular ball bearing or a deep groove ball bearing.

It is sectional drawing which shows the rolling bearing apparatus which concerns on embodiment of this invention. It is an expanded sectional view of the principal part of the rolling bearing apparatus in FIG. FIG. 3 is an enlarged side view of an inner ring in FIG. 2. It is the sectional view on the AA line in FIG. It is sectional drawing which shows the rolling bearing apparatus which concerns on other embodiment of this invention. It is principal part sectional drawing which shows a prior art example. It is principal part sectional drawing which shows a prior art example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Rolling bearing apparatus 11 1st tapered roller bearing (rolling bearing)
15 Output shaft (inner shaft)
15a Step surface (opposite surface)
25 First housing (housing)
25c Inner end face (opposite face)
32 Outer ring 32a Inner circumferential raceway surface 32b Outer circumferential surface 32c Left end surface (opposing surface)
33 Inner ring 33a Outer raceway surface 33b Tapered groove 33c End face of the large flange (opposing surface)
34 Tapered rollers (rolling elements)
35 pressing member 36 biasing member 40 preload holding means

Claims (3)

Rolling elements,
An outer ring having a raceway surface on the inner periphery for receiving the radial load from the rolling element and the load directed to one side in the axial direction while the rolling element rolls;
An inner ring that has a raceway surface on which the rolling element rolls on the outer periphery and is incorporated in an outer ring via the rolling element in a state in which a preload is applied;
A housing having an outer peripheral surface of the outer ring fitted therein and having a first linear expansion coefficient;
The inner ring has an inner circumferential surface that is fitted in a state in which relative movement in the axial direction and the circumferential direction is allowed, and has an opposing surface that faces an end surface on the other axial side of the inner ring, and A rotating shaft having a second linear expansion coefficient smaller than the linear expansion coefficient of 1;
A taper groove extending in the circumferential direction provided on at least one of the end surface on the other axial side of the inner ring and the opposite surface of the rotation shaft, a pressing member introduced into the taper groove so as to be capable of rolling, and a taper groove A biasing member that is introduced and thermally expands as the temperature rises and biases the pressing member in the circumferential direction, and the relative movement in the circumferential direction between the inner ring and the rotating shaft and the biasing Preload holding means that presses the inner ring toward one side in the axial direction by rolling the pressing member along the tapered groove by urging by the member, and suppresses a decrease in the preload due to thermal expansion of the housing; A rolling bearing device comprising: Rolling elements,
An outer ring having a raceway surface on the inner periphery for receiving the radial load from the rolling element and the load directed to one side in the axial direction while the rolling element rolls;
An inner ring that has a raceway surface on which the rolling element rolls on the outer periphery and is incorporated in an outer ring via the rolling element in a state in which a preload is applied;
The outer ring has an outer peripheral surface that is fitted in a state in which relative movement in the axial direction and the circumferential direction is allowed, and has an opposing surface that faces an end surface on one axial side of the outer ring, and A housing having a linear expansion coefficient;
A rotating shaft having an inner peripheral surface of the inner ring fitted therein and having a second linear expansion coefficient smaller than the first linear expansion coefficient;
A taper groove extending in the circumferential direction provided on at least one of the end surface on the one axial side of the outer ring and the opposing surface of the housing, a pressing member introduced into the taper groove in a rollable manner, and introduced into the taper groove And a biasing member that thermally expands as the temperature rises and biases the pressing member in the circumferential direction, and is provided with a relative movement in the circumferential direction between the outer ring and the housing and by the biasing member. Preload holding means for pressing the outer ring toward the other side in the axial direction by rolling the pressing member along the tapered groove by urging to suppress a decrease in the preload due to thermal expansion of the housing. A rolling bearing device characterized by that.   The rolling bearing device according to claim 1, wherein the urging member is made of a bimetal.

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