JP2021169843A - Rolling bearing device - Google Patents

Abstract

To prevent damage of an elastic member in a rolling bearing device which prevents creep of an outer ring.SOLUTION: A rolling bearing device 50 includes a housing 80 and a rolling bearing 10. A bearing fitting part 82 of the housing 80 includes a bearing fitting surface 84 and a chamfered part 87 formed at an opening side end part. The rolling bearing 10 includes: an outer ring 11; an inner ring 12; rolling elements 13; and an annular elastic member 15. The outer ring 11 has: a bearing outer diameter surface 17; a side surface 18 extending in a radial direction at one side in an axial direction; and an annular recessed part 30 formed over an entire periphery in a portion where the side surface 18 and the bearing outer diameter surface 17 are connected. The elastic member 15 integrally has a body part 41 and a protruding part 42 protruding to one side in the axial direction. An angle β formed between a tangent line which contacts the body part 41 and the protruding part 42 at the radial outer side and a center axis is smaller than an angle α formed between a generating line of the chamfered part 87 and the center axis.SELECTED DRAWING: Figure 1

Description

The present invention relates to a rolling bearing device mainly used for a vehicle driving device, and more particularly to a rolling bearing device in which an elastic member is fixed to an outer ring to prevent creep with respect to a housing.

In drive devices such as vehicle transmissions and differentials, as shown in FIG. 8, the gear shaft 81 is rotatably supported by a rolling bearing device in which rolling bearings 70 and 70 are incorporated in a housing 80. The rolling bearing 70 includes an outer ring 71 and an inner ring 72 that rotate relatively around the central axis m, and the outer ring 71 is fixed to the bearing fitting portion 82 of the housing 80 in a clearance-fitted state. .. However, since the housing 80 is made of cast aluminum and has a coefficient of thermal expansion larger than that of the rolling bearing 70 made of steel, when the vehicle travels and the temperature of the housing 80 rises, the outer ring 71 and the bearing fitting portion 82 are fitted. The gap between the mating surfaces expands.

Normally, in a state in which the vehicle is driven by an engine (driving state), the reaction force of the power transmitted by the gear acts on the rolling bearing 70, so that the outer ring 71 is strongly pressed against the housing 80. It does not rotate easily. However, when the accelerator is released and the wheels switch to the state of driving the engine (coast state), the rolling bearing 70 becomes a no-load state. At this time, if the clearance between the outer ring 71 and the fitting surface of the bearing fitting portion 82 is large, the outer ring 71 rotates due to the drag resistance of the rolling bearing 70, so that the fitting surface of the housing 80 may be worn. .. The drag resistance refers to a force that rotates the outer ring 71 due to the viscosity of the oil that lubricates the rolling bearing 70, rolling friction, or the like when the inner ring 72 rotates. In the following description, the rotation of the outer ring 71 inside the bearing fitting portion 82 in this way is referred to as “creep”.

In the rolling bearing device of Patent Document 1, as shown in FIG. 9, a rubber O-ring 73 is incorporated in a recess 74 provided on the outer periphery of the outer ring 71, and sliding friction between the O-ring 73 and the housing 80 is provided. A configuration is described in which the creep of the outer ring 71 is suppressed by a force.

Japanese Unexamined Patent Publication No. 08-074845

However, in the rolling bearing device of Patent Document 1, since the recess 74 is formed at the axial end of the outer ring 71, when the outer ring 71 is fitted to the housing 80, the center of the bearing fitting portion 82 and the rolling bearing 70 If the center is largely eccentric, the end of the bearing fitting portion 82 on the opening side collides with the O-ring 73. Therefore, the O-ring 73 may be damaged or cut by being sandwiched between the housing 80 and the outer ring 71.

Therefore, as shown in FIG. 10, a method is conceivable in which the O-ring 73 is arranged at a position closer to the center in the width direction of the outer ring 71 to prevent the open end of the housing 80 and the O-ring 73 from coming into direct contact with each other. .. However, in this case, since the recess 74 accommodating the O-ring 73 is close to the raceway surface 75 of the outer ring 71, the wall thickness t between the recess 74 and the raceway surface 75 is reduced. Therefore, when a large load acts on the rolling bearing 70, the internal stress increases at a place where the wall thickness t is small, and the outer ring 71 may be damaged.

In view of the above circumstances, an object of the present invention is to prevent damage to the elastic member when it is assembled to the housing in a rolling bearing device in which an elastic member is attached to the outer periphery of the outer ring to prevent creep of the outer ring with respect to the housing. I am aiming.

The present invention is a rolling bearing device including a housing provided with a bearing fitting portion and a rolling bearing incorporated in the bearing fitting portion to rotatably support a shaft around a central shaft. The bearing fitting portion has a cylindrical bearing fitting surface having a chamfered portion at an end thereof, and the rolling bearing includes a plurality of rolling bearings arranged between an outer ring, an inner ring, and the outer ring and the inner ring. It has a rolling element and an annular elastic member centered on a central axis, and the elastic member has a main body portion having a circular cross section in the central axis direction and a main body having a diameter smaller than the inner diameter of the bearing fitting surface. A convex portion that protrudes from the portion in the direction of the central axis is integrally provided, and the convex portion is incorporated in a portion where the outer diameter surface of the bearing of the outer ring and one side surface in the axial direction are connected so that the convex portion is directed to one side in the axial direction. In the plane including the central axis, the angle α between the tangent line and the central axis that are in contact with the main body portion and the convex portion in the radial direction is smaller than the angle β between the mother line and the central axis of the chamfered portion. When the rolling bearing is incorporated into the housing, the elastic member and the chamfered portion are combined so as to face each other in the axial direction.

According to the present invention, in a rolling bearing device in which an elastic member is attached to the outer periphery of the outer ring to prevent creep of the outer ring with respect to the housing, even if the amount of eccentricity is large when assembling to the housing, the elastic member is damaged. Can be prevented.

It is a partial cross-sectional view of the rolling bearing apparatus which concerns on one Embodiment of this invention. FIG. 1 is an enlarged view of a main part of a portion in which an elastic member is incorporated. FIG. 3A is a partial front view of the elastic member, and FIG. 3B is an axial cross-sectional view. It is explanatory drawing explaining the position of the elastic member when a rolling bearing is assembled coaxially with a housing. It is explanatory drawing explaining the position of the elastic member when a rolling bearing is eccentrically incorporated with a housing. FIG. 6A is a partial front view of an elastic member of another form, and FIG. 6B is an axial cross-sectional view. It is a partial cross-sectional view of the rolling bearing which incorporated the elastic member of another form. It is sectional drawing of the conventional rolling bearing apparatus. It is sectional drawing in the axial direction of the conventional rolling bearing. It is an axial sectional view which shows the other form of the conventional rolling bearing.

A mode for carrying out the present invention will be described with reference to the drawings. FIG. 1 is a partial cross-sectional view of a transmission in which a rolling bearing device 50 as an embodiment of the present invention (hereinafter referred to as “the present embodiment”) is incorporated. The rolling bearing device 50 includes a housing 80 and a rolling bearing 10, and the rolling bearing 10 is incorporated in the housing 80 to rotatably support the gear shaft 81. Although not shown, the gear shaft 81 is rotatably supported by rolling bearings 10 at both ends in the axial direction, similarly to a conventional transmission (see FIG. 8). FIG. 1 shows an assembled state of one rolling bearing 10 in the axial direction.

The rolling bearing 10 is a tapered roller bearing. The rolling bearings 10 and 10 at both ends of the gear shaft 81 in the axial direction are incorporated so that their front surfaces face each other. In the following description, the direction parallel to the central axis m, which is the center of rotation of the rolling bearing 10, is referred to as the axial direction, the direction orthogonal to the central axis m is referred to as the radial direction, and the direction orbiting around the central axis m is referred to as the circumferential direction. Further, the left side of FIG. 1 is referred to as one in the axial direction, and the right side is referred to as the other in the axial direction.

The housing 80 is made of a light alloy such as cast aluminum. The housing 80 includes a bearing fitting portion 82 for assembling the rolling bearing 10.
The bearing fitting portion 82 is a bottomed cylindrical hole recessed in one axial direction from the inner peripheral surface 83 of the housing 80. The bearing fitting portion 82 includes a bearing fitting surface 84 and a contact surface 85, and is open to the other in the axial direction.
The bearing fitting surface 84 is a cylindrical surface centered on the central axis m, and the bearing outer diameter surface 17 of the outer ring 11 is fitted as described later. The contact surface 85 is formed in a direction orthogonal to the central axis m, and extends inward in the radial direction from one end in the axial direction of the bearing fitting surface 84. The contact surface 85 abuts on the outer ring 11 of the rolling bearing 10 to regulate the axial position of the rolling bearing 10.
An inclined surface 87 as a chamfered portion is provided at the opening side end of the bearing fitting surface 84. FIG. 1A is an enlarged view of a main part of the bearing fitting surface 84 on the opening side. The inclined surface 87 is a part of a conical surface and connects the bearing fitting surface 84 and the inner peripheral surface 83 of the housing 80. The inner diameter of the inclined surface 87 increases toward the opening side (the other side in the axial direction in the drawing).

The rolling bearing 10 includes an outer ring 11, an inner ring 12, a plurality of tapered rollers 13 as rolling elements, a cage 14, and an elastic member 15.
The outer ring 11 and the inner ring 12 are annular and are combined so that their central axes coincide with each other. The plurality of tapered rollers 13 are rotatably incorporated between the outer ring 11 and the inner ring 12, and the inner ring 12 can freely rotate around the central axis m inside the outer ring 11.

The outer ring 11 is made of a steel material such as a bearing steel such as SUJ2. The outer ring 11 includes an outer raceway surface 16, a bearing outer diameter surface 17, an outer ring large end surface 18, an outer ring small end surface 19, and a recess 30.

The outer raceway surface 16 is a raceway surface formed on the inner circumference of the outer ring 11 and on which the tapered rollers 13 roll. The outer raceway surface 16 is formed of a conical surface centered on the central axis m, and its diameter decreases toward one side in the axial direction.
The bearing outer diameter surface 17 is a cylindrical surface centered on the central axis m.
The outer ring large end surface 18 is formed on one side surface of the outer ring 11 in the axial direction in a direction orthogonal to the central axis m and extends in the radial direction. The radial inner end of the outer ring large end surface 18 is connected to one axial end of the outer raceway surface 16.
The outer ring small end surface 19 is formed on the other side surface of the outer ring 11 in the axial direction in a direction orthogonal to the central axis m, and the other end portion in the axial direction of the bearing outer diameter surface 17 and the other end surface in the axial direction of the outer raceway surface 16. The ends of the bearings are connected in the radial direction.

The recess 30 will be described with reference to FIG. FIG. 2 is an enlarged partial cross-sectional view of the region including the recess 30 in FIG. The recess 30 is formed in an annular shape over the entire circumference at a portion where the outer periphery of the outer ring large end surface 18 and the bearing outer diameter surface 17 are connected, and is defined by a groove bottom surface 31, a protrusion 32, and a groove side surface 33. An elastic member 15 is assembled to the recess 30 as described later.

The groove bottom surface 31 is a cylindrical surface centered on the central axis m, and the outer diameter of the groove bottom surface 31 is smaller than the outer diameter of the bearing outer diameter surface 17.
A protruding portion 32 that projects outward in the radial direction is formed at one end of the groove bottom surface 31 in the axial direction. The projecting portion 32 includes an outer peripheral surface 34 of the projecting portion, and a first side surface 35 and a second side surface 36 on both sides in the axial direction. The protruding portion outer peripheral surface 34 is a cylindrical surface extending in the axial direction, and has a diameter larger than the outer diameter of the groove bottom surface 31. The first side surface 35 is formed in one axial direction of the outer peripheral surface 34 of the protruding portion and extends in the radial direction, and is flush with the large end surface 18 of the outer ring. The second side surface 36 connects the other end in the axial direction of the outer peripheral surface 34 of the protruding portion and one end in the axial direction of the bottom surface 31 of the groove, and is inclined in the axial direction.
The protrusion 32 prevents the elastic member 15 from falling out of the recess 30. Therefore, the height h at which the protruding portion 32 protrudes radially from the groove bottom surface 31 may be such that it does not easily get over when the elastic member 15 moves in the axial direction. For example, the groove bottom surface 31 and the outside of the bearing. It is set to about 10 to 20% of the radial dimension H with respect to the radial surface 17.
The groove side surface 33 extends radially outward from the other end of the groove bottom surface 31 in the axial direction in a direction orthogonal to the central axis m, and is connected to one end of the bearing outer diameter surface 17 in the axial direction. There is.

In this way, the recess 30 is formed by denting inward in the radial direction from one end in the axial direction of the outer diameter surface 17 of the bearing and denting inward in the axial direction from the outward end in the radial direction of the large end surface 18 of the outer ring. .. In this way, since the recess 30 is open outward in the radial direction and one in the axial direction, it can be easily formed by cutting.

See FIG. 1 again. The inner ring 12 is made of a steel material such as a bearing steel such as SUJ2. The inner ring 12 includes an inner raceway surface 20, a bearing inner diameter surface 21, an inner ring small end surface 22, and an inner ring large end surface 23.

The inner raceway surface 20 is formed on the outer circumference of the inner ring 12, and is a raceway surface on which the tapered rollers 13 roll. The inner raceway surface 20 is formed of a conical surface centered on the central axis m, and its diameter decreases toward one side in the axial direction. A small brim 24 that is convex outward in the radial direction is formed at one end of the inner raceway surface 20 in the axial direction, and is convex outward in the radial direction at the other end in the axial direction of the inner raceway surface 20. The large brim 25 is formed. The tapered roller 13 is guided by the large brim 25 when the rolling bearing 10 rotates, and rolls in the circumferential direction.
The bearing inner diameter surface 21 is a cylindrical surface centered on the central axis m. The inner ring small end surface 22 extends radially from one end of the bearing inner diameter surface 21 in the axial direction, and the inner ring large end surface 23 extends radially from the other end of the bearing inner diameter surface 21 in the axial direction. doing.

The tapered roller 13 is made of a steel material such as a bearing steel such as SUJ2. The tapered rollers 13 have the shape of a truncated cone, and a plurality of tapered rollers 13 are incorporated between the outer raceway surface 16 of the outer ring 11 and the inner raceway surface 20 of the inner ring 12.

The cage 14 is manufactured by press-molding a cold-rolled steel sheet or injection-molding a synthetic resin. The cage 14 is formed with a plurality of pockets for accommodating tapered rollers 13 one by one in the circumferential direction. The plurality of tapered rollers 13 are held by the cage 14 between the inner ring 12 and the outer ring 11 at equal intervals in the circumferential direction.

When the inner ring 12 or the outer ring 11 rotates, the tapered rollers 13 roll on the raceway surfaces 16 and 20, respectively. Since each of the raceway surfaces 16 and 20 is formed of a conical surface, the rolling bearing 10 can simultaneously support a load acting in the axial direction (axial load) and a load acting in the radial direction (radial load).

The elastic member 15 will be described with reference to FIG. FIG. 3A is a front view of the elastic member 15 viewed in the axial direction, and FIG. 3B is a cross-sectional view taken along the line YY of FIG. 3A.
The elastic member 15 has an annular shape centered on the central axis m and has a uniform thickness in the circumferential direction. The elastic member 15 is made of an oil-resistant rubber material such as nitrile rubber (NBR) or acrylic rubber (ACM), and the main body portion 41 and the convex portion 42 are integrally formed. The main body 41 has a substantially circular cross section in the axial direction. The convex portion 42 is formed in one of the axial directions of the main body portion 41 over the entire circumference of the elastic member 15, and has a rectangular cross section in the axial direction.

The outer peripheral surface of the main body 41 (hereinafter referred to as “main body outer peripheral surface 43”) is formed by a part of a circle having a diameter d in the axial cross section.
The convex portion 42 includes a convex portion side surface 44, a convex portion outer peripheral surface 45, and a convex portion inner peripheral surface 46. The convex portion side surface 44 extends in the radial direction at right angles to the central axis m. The convex portion outer peripheral surface 45 is a cylindrical surface extending axially from the radial outer end of the convex portion side surface 44 and connecting to the main body outer peripheral surface 43. The outer diameter of the outer peripheral surface 45 of the convex portion is smaller than the outer diameter of the main body 41 and smaller than the inner diameter of the bearing fitting surface 84 of the housing 80.

In this way, the elastic member 15 is formed with a point having the maximum outer diameter (indicated by point Q in FIG. 2) and a point having the minimum inner diameter (indicated by point P in FIG. 2) in the main body 41. There is. In the free state, the elastic member 15 has an inner peripheral peripheral length (which is the length in the circumferential direction at the position of the point P) shorter than the peripheral length of the groove bottom surface 31. Therefore, when the elastic member 15 is assembled to the recess 30, the main body 41 is elastically pressed against the groove bottom surface 31 over the entire circumference.

The radial thickness w1 of the elastic member 15 is larger than the radial dimension H of the groove bottom surface 31 and the bearing outer diameter surface 17 of the outer ring 11. The radial thickness w1 is halved of the difference between the outer diameter and the inner diameter of the elastic member 15, and is equal to the diameter d of the main body 41. When the elastic member 15 is assembled in the recess 30, a part of the main body 41 projects radially outward from the bearing outer diameter surface 17. In FIG. 2, the height at which the main body 41 protrudes from the bearing outer diameter surface 17 is indicated by s.

The axial thickness w2 of the elastic member 15 is smaller than the axial dimension L of the outer ring large end surface 18 and the groove side surface 33. The axial thickness w2 means the axial dimension of the apex R and the convex side surface 44 of the other main body outer peripheral surface 43 in the axial direction. When the elastic member 15 is assembled in the recess 30, the elastic member 15 does not protrude in one axial direction from the outer ring large end surface 18.

The contact state between the housing 80 and the elastic member 15 when the rolling bearing 10 is incorporated into the bearing fitting portion 82 will be described with reference to FIGS. 4 and 5.
FIG. 4 shows how the elastic member 15 comes into contact with the opening-side end of the bearing fitting 82 when the rolling bearing 10 and the bearing fitting 82 are coaxially assembled. FIG. 5 shows a state in which the opening side end portion of the bearing fitting portion 82 and the elastic member 15 come into contact with each other when the rolling bearing 10 and the bearing fitting portion 82 are assembled in an eccentric manner.

First, the contact state between the housing 80 and the elastic member 15 when the rolling bearing 10 and the bearing fitting portion 82 are coaxially assembled will be described with reference to FIG.
The rolling bearing 10 is inserted into the bearing fitting portion 82 with the outer ring large end surface 18 facing one axial direction. The diameter of the bearing fitting surface 84 is slightly larger than the diameter of the bearing outer diameter surface 17 of the rolling bearing 10 at room temperature, and the rolling bearing 10 is assembled to the bearing fitting portion 82 in a clearance-fitted state. ..
Further, the elastic member 15 incorporated in the recess 30 projects radially outward from the bearing outer diameter surface 17 by the height s (see FIG. 2).

The outer diameter of the convex outer peripheral surface 45 of the elastic member 15 is smaller than the outer diameter of the main body 41 and smaller than the inner diameter of the bearing fitting surface 84 of the housing 80. Therefore, when the rolling bearing 10 is inserted into the bearing fitting portion 82, the housing 80 and the convex portion 42 do not come into contact with each other, and the main body portion 41 abuts on the inclined surface 87 of the housing 80 in the axial direction. .. After that, as the rolling bearing 10 moves in the axial direction, the main body 41 is displaced along the inclined surface 87 and compressed in the radial direction. At this time, since the height s compressed in the radial direction is small, the elastic member 15 is easily compressed and deformed in the radial direction and incorporated inside the bearing fitting surface 84, so that the elastic member 15 is not damaged.
When the rolling bearing 10 is incorporated into the bearing fitting portion 82, the elastic member 15 is sandwiched in the radial direction between the bearing fitting surface 84 and the groove bottom surface 31, and is elastically compressed in the radial direction by the height s. It is incorporated in the state of being.

The rolling bearing 10 is positioned in the axial direction when the outer ring large end surface 18 abuts on the contact surface 85 in the axial direction. Similarly, the rolling bearing 10 is positioned and assembled in the axial direction on the other side of the gear shaft 81 in the axial direction. In this way, the rolling bearings 10 and 10 that support both ends of the gear shaft 81 in the axial direction are incorporated in a state where preload is applied in the axial direction to each other.

Since the axial thickness w2 of the elastic member 15 is set smaller than the axial dimension L of the outer ring large end surface 18 and the groove side surface 33, the elastic member 15 is compressed only in the radial direction. It has become. This is to prevent the elastic member 15 from being compressed in the radial direction and the axial direction to fill the inside of the recess 30 and causing an axial assembly failure of the rolling bearing 10. However, when the recess 30 is set sufficiently large, it does not prevent the elastic member 15 from projecting from the outer ring large end surface 18 in one axial direction.

When the temperature of the transmission rises, the housing 80, the gear shaft 81, and the rolling bearing 10 expand in the axial and radial directions, respectively. The housing 80 is made of aluminum and has a coefficient of linear expansion of approximately 18 to 25 × ^10-6 , the gear shaft 81 and the rolling bearing 10 are made of steel, and the coefficient of linear expansion is approximately 10 to 13 × ^10-6. Is. Therefore, the amount of axial thermal expansion of the housing 80 (equal to the amount of increase in the axial dimension of one bearing fitting portion 82 and the other bearing fitting portion 82) is the amount of axial thermal expansion of the gear shaft 81. Since it is larger than the amount, the preload in the axial direction of the rolling bearing 10 is reduced. Further, since the amount of thermal expansion of the inner diameter of the bearing fitting surface 84 is larger than the amount of thermal expansion of the outer diameter of the outer ring 11, the clearance between the bearing outer diameter surface 17 of the outer ring 11 and the bearing fitting surface 84 of the housing 80 is expanded. do. The difference Δ between the thermal expansion amount of the inner diameter of the bearing fitting surface 84 and the thermal expansion amount of the outer diameter of the bearing outer diameter surface 17 is approximately 0.1 mm or less (0.05 mm or less in radius).

In the present embodiment, the elastic member 15 is incorporated in a state of being compressed by a height s in the radial direction. The height s is set to be larger than the difference Δ between the amount of thermal expansion of the inner diameter of the bearing fitting surface 84 and the amount of thermal expansion of the outer diameter of the bearing outer diameter surface 17 due to the increase in the temperature of the transmission. Therefore, the elastic member 15 can always maintain a state of being elastically compressed between the bearing fitting surface 84 and the groove bottom surface 31.

As a result, even if the gap between the bearing outer diameter surface 17 of the outer ring 11 and the bearing fitting surface 84 of the housing 80 is widened, the gap between the elastic member 15 and the bearing fitting surface 84 and the elastic member 15 are always present. A sliding frictional force is generated between the groove bottom surface 31 and the groove bottom surface 31. This frictional force can prevent creep of the outer ring 11.

As described above, when the rolling bearing 10 is inserted into the bearing fitting portion 82, it is preferably fitted coaxially. However, when the rolling bearing 10 is actually fitted to the inner circumference of the bearing fitting surface 84, the rolling bearing 10 may be displaced from each other in the radial direction. When the eccentricity amount δ is large, the elastic member 15 may be deformed or cut due to strong contact with the housing 80.
In the present embodiment, the elastic member 15 is provided with the convex portion 42 to prevent the elastic member 15 from being damaged when the rolling bearing 10 is assembled to the bearing fitting portion 82 of the housing 80. This will be described with reference to FIG.

As shown in FIG. 5, the contact state between the housing 80 and the elastic member 15 when the rolling bearing 10 and the bearing fitting portion 82 are eccentrically assembled by δ will be described. In FIG. 5, the position of the bearing fitting portion 82 coaxial with the rolling bearing 10 is shown by a broken line.
In the present embodiment, the outer diameter of the convex outer peripheral surface 45 of the elastic member 15 is smaller than the outer diameter of the main body 41 and smaller than the inner diameter of the bearing fitting surface 84 of the housing 80. As a result, in the plane including the central axis m, the angle α formed by the tangent line n that is in contact with the main body portion 41 and the convex portion 42 radially outward and the central axis m is the home line and the center of the conical surface forming the inclined surface 87. It is set smaller than the angle β formed by the axis m. In the present embodiment, the tangent line n is in contact with the corner portion A connecting the convex portion side surface 44 and the convex portion outer peripheral surface 45 with respect to the convex portion 42.

Therefore, when the housing 80 and the elastic member 15 come close to each other when the eccentricity amount δ is large, the convex portion 42 and the inclined surface 87 always come into contact with each other before the main body portion 41 and the inclined surface 87 come into contact with each other. When the rolling bearing 10 further moves in the axial direction in this state, the convex portion 42 is urged inward in the radial direction along the inclined surface 87, and the eccentricity δ between the rolling bearing 10 and the bearing fitting portion 82 is reduced. do. After that, since the inclined surface 87 and the main body 41 come into contact with each other, the force of contact between the main body 41 and the inclined surface 87 is relaxed, and the elastic member 15 is easily compressed and deformed in the radial direction to form the bearing fitting surface 84. Incorporated inside.
On the other hand, if it is assumed that the elastic member 15 is formed only by the main body 41 having a circular cross section in the axial direction without providing the convex portion 42, the inclined surface 87 is the main body. Since it comes into strong contact with 41, the main body 41 may be sandwiched between the inclined surface 87 and the outer ring 11 and may be deformed or cut.

As described above, in the rolling bearing 10 of the present embodiment, when the rolling bearing device 50 in which the elastic member 15 is attached to the outer periphery of the outer ring 11 to prevent the outer ring 11 from creeping with respect to the housing 80, is assembled to the housing 80. Even when the eccentricity amount δ is large, the main body 41 of the elastic member 15 is prevented from being pinched between the housing 80 and the outer ring 11, and damage such as cutting of the elastic member 15 is prevented. Can be done.

In the elastic member 15 of the present embodiment, the convex portion 42 is continuously formed in the circumferential direction. However, the present invention is not limited to this, and as shown in FIG. 6, the convex portion 42a may be formed intermittently in the circumferential direction. FIG. 6A is a front view of the elastic member 15a viewed in the axial direction, and FIG. 6B is a cross-sectional view taken along the line YY of FIG. 6A.
Further, in the elastic member 15 of the present embodiment, the convex portion 42 is formed only in one of the axial directions of the main body portion 41, but as in the elastic member 15b shown in FIG. 7, the convex portion 42 is the main body portion 41. It may be formed on both sides in the axial direction. FIG. 7 is an axial cross-sectional view similar to that of FIG. 2 for the rolling bearing 10 incorporating the elastic member 15b. When the elastic member 15b is used, it is not necessary to pay attention to the axial direction when assembling the elastic member 15b to the rolling bearing 10, so that the assembling property can be improved.

Although the embodiments of the present invention have been described above, the above-described embodiments are merely examples for carrying out the present invention. The present invention is not limited to the above-described embodiment, and the above-described embodiment can be appropriately modified and implemented without departing from the spirit of the present invention. For example, in the present embodiment, as the rolling bearing, a tapered roller bearing in which the rolling element is a tapered roller has been described, but an angular contact ball bearing or a double row ball bearing in which the rolling element is a ball may be used. Further, the case where the rolling bearing is assembled to the aluminum housing has been described, but when the preload fluctuation with respect to the rolling bearing is unlikely to occur as in the case where the gear shaft and the housing are made of a material having an approximate linear expansion coefficient. However, the rolling bearings of the present invention can be used only for the purpose of preventing creep of the outer ring. Further, the rolling bearing of the present invention is not limited to the case where it is used for a vehicle transmission, and can be used in various places.

(Implementation) 10: Rolling bearing, 11: Outer ring, 12: Inner ring, 13: Tapered roller, 14: Cage, 15: Elastic member, 16: Outer raceway surface, 17: Bearing outer diameter surface, 18: Outer ring size End face, 19: Outer ring small end face, 20: Inner raceway surface, 21: Bearing inner diameter surface, 22: Inner ring small end face, 23: Inner ring large end face, 24: Small brim, 25: Large brim, 30: Recess, 31: Groove bottom surface , 32: Protruding part, 33: Groove side surface, 34: Protruding part outer peripheral surface, 35: First side surface, 36: Second side surface, 41: Main body part, 42: Convex part, 43: Main body outer peripheral surface, 44: Convex part Side surface, 45: outer peripheral surface of convex portion, 46: inner peripheral surface of convex portion, 50: rolling bearing device,
(Prior art) 70: Rolling bearing, 71: Outer ring, 72: Inner ring, 73: O-ring, 74: Recessed, 75: Track surface, 80: Housing, 81: Gear shaft, 82: Bearing fitting part, 83: Inner Peripheral surface, 84: Bearing fitting surface, 85: Contact surface, 87: Inclined surface

Claims (4)

A rolling bearing device including a housing provided with a bearing fitting portion and a rolling bearing incorporated in the bearing fitting portion to rotatably support a shaft around a central shaft.
The bearing fitting portion has a cylindrical bearing fitting surface having a chamfered portion at an end thereof.
The rolling bearing has an outer ring, an inner ring, a plurality of rolling elements arranged between the outer ring and the inner ring, and an annular elastic member centered on a central axis.
The elastic member integrally has a main body portion having a circular cross section in the central axis direction and a convex portion having a diameter smaller than the inner diameter of the bearing fitting surface and protruding from the main body portion in the direction of the central axis. The convex portion is incorporated in a portion where the outer diameter surface of the bearing of the outer ring and one side surface in the axial direction are connected so that the convex portion is directed to one side in the axial direction.
In the plane including the central axis, the angle α between the tangent line and the central axis that are in contact with the main body portion and the convex portion radially outward is smaller than the angle β between the generatrix and the central axis of the chamfered portion.
A rolling bearing device in which the elastic member and the chamfered portion are combined in an axially opposed direction when the rolling bearing is incorporated into the housing. The rolling bearing device according to claim 1, wherein a plurality of the convex portions are formed intermittently in the circumferential direction. The rolling bearing device according to claim 1, wherein the convex portion is continuously formed in an annular shape in the circumferential direction. The rolling bearing device according to any one of claims 1 to 3, wherein the convex portions are formed on both sides in the axial direction.

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