JP7112201B2 - Rolling bearing seals and rolling bearings - Google Patents

Description

The present invention relates to a rolling bearing seal for sealing between an inner ring and an outer ring of a rolling bearing and a rolling bearing equipped with this seal.

Rolling bearings are equipped with a seal that seals between the inner and outer rings to prevent the intrusion of foreign matter such as dust and dirt from the outside, as well as the leakage of the grease sealed inside the bearing. There are also sealed rolling bearings. Sealed rolling bearings generally have an annular seal made of a rubber seal member reinforced by a core metal fixed to one of the inner ring and the outer ring, and the lip portion of the seal member is brought into contact with the other. It seals the space. By devising the shape of the lip of the seal member, etc., the sliding resistance (rotational torque of the bearing) is reduced while improving the sealing performance.

For example, Patent Document 1 discloses a seal device in which a main lip that contacts the outer peripheral surface of an inner ring is formed on the axial inner side of a seal member, and a non-contact portion that forms a labyrinth seal with the inner ring is formed on the outer side. is disclosed. The labyrinth seal at the non-contact portion of the seal device reduces external pressure acting on the main lip and prevents foreign matter from entering. Prevents uneven wear.

JP-A-2006-97851

However, in the sealing device described in Patent Document 1, since the main purpose is to cope with external high pressure, the core bar extends to the vicinity of the tip of the main lip, and the base of the main lip extends. Since the structure is thick and hard to bend, the sliding resistance between the main lip and the inner ring increases, and the rotational torque of the rolling bearing increases.

SUMMARY OF THE INVENTION The present invention has been made in view of the above points, and provides a rolling bearing seal and a rolling bearing with seal that can reduce sliding resistance (rotational torque of the bearing) while maintaining necessary sealing performance. intended to

In order to solve the above problems, the rolling bearing seal of the invention according to claim 1 is an annular rolling bearing seal that is fixed to the outer ring of the rolling bearing and seals between the inner ring and the outer ring,
An annular core bar extending between the inner ring and the outer ring, and an elastic member covering at least a portion of the core bar,
The elastic member has a seal portion that covers the inner surface and the outer surface of the rolling bearing in the axial direction of the inner peripheral portion of the core bar,
The seal portion has a thick portion that is thicker than a portion covering the outer surface of the core bar and covers the inner surface of the core bar,
An auxiliary lip that is not in contact with the outer peripheral surface of the inner ring with a gap and a main lip that contacts the outer peripheral surface of the inner ring axially inwardly of the auxiliary lip are formed on the inner peripheral portion of the seal portion. is,
An annular groove opening axially inward is provided between the thick portion of the seal portion and the main lip, and a thin flexible portion is formed at the base of the main lip. A tip of the main lip that contacts the outer peripheral surface of the inner ring is formed radially inward of the thick portion ,
The thick portion is provided continuously with the annular groove at a position that regulates the amount of deflection of the main lip .
The rolling bearing seal of the invention according to claim 2 is an annular rolling bearing seal that is fixed to the inner ring of the rolling bearing and seals between the inner ring and the outer ring,
An annular core bar extending between the inner ring and the outer ring, and an elastic member covering at least a portion of the core bar,
The elastic member has a seal portion that covers the inner surface and the outer surface in the axial direction of the rolling bearing on the outer peripheral portion of the core bar,
The seal portion has a thick portion that is thicker than a portion covering the outer surface of the core bar and covers the inner surface of the core bar,
An auxiliary lip that is not in contact with the inner peripheral surface of the outer ring with a gap and a main lip that contacts the inner peripheral surface of the outer ring axially inwardly of the auxiliary lip is formed on the outer peripheral portion of the seal portion. formed,
An annular groove opening axially inward is provided between the thick portion of the seal portion and the main lip, and a thin flexible portion is formed at the base of the main lip. A tip of the main lip that contacts the inner peripheral surface of the outer ring is formed radially outward of the thick portion ,
The thick portion is provided continuously with the annular groove at a position that regulates the amount of deflection of the main lip .
According to a third aspect of the invention, there is provided a rolling bearing seal according to the first or second aspect of the invention, characterized in that the tip of the auxiliary lip is arranged at a position where the position in the axial direction overlaps with the core metal. do.
According to a fourth aspect of the present invention, there is provided a rolling bearing seal according to any one of the first to third aspects, wherein the outer surface of the distal end portion of the auxiliary lip in the axial direction of the rolling bearing; The inclination angle between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring, which are not in contact with each other with a gap, is the inner surface of the tip of the auxiliary lip in the axial direction of the rolling bearing and the auxiliary lip portion is smaller than the inclination angle between the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring that is not in contact with a gap.
According to a fifth aspect of the present invention, there is provided a rolling bearing seal according to any one of the first to fourth aspects, wherein the inner surface of the tip portion of the main lip in the axial direction of the rolling bearing and the main lip The inclination angle between the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring with which the main lip portion contacts with the outer surface of the tip portion of the main lip in the axial direction of the rolling bearing It is characterized by being smaller than the inclination angle between the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring.
According to a sixth aspect of the invention, there is provided a rolling bearing equipped with the rolling bearing seal according to any one of the first to fifth aspects.

According to the inventions of claims 1 and 2, the auxiliary lip suppresses foreign matter such as dust and moisture from entering between the inner ring and the outer ring, and reduces external pressure acting on the main lip. , the main lip seals between the inner ring and the outer ring. By providing the annular groove between the thick portion of the seal portion and the main lip and forming the thin flexible portion at the base portion of the main lip, the sliding resistance of the main lip can be reduced. By forming the non-contact auxiliary lip on the inner peripheral side (claim 1) or the outer peripheral side (claim 2) of the core bar, the rigidity is increased, and stable sealing performance can be obtained. Further, by providing the thick portion inside the core in the axial direction, it is possible to increase the rigidity of the entire seal, obtain stable sealing performance, and improve the bonding between the elastic member and the core. Furthermore, since the thick portion is provided continuously with the annular groove, the main lip is prevented from being turned up and the grease inside the bearing is prevented from excessively adhering to the main lip.
According to the third aspect of the invention, it is possible to effectively suppress the intrusion of foreign substances such as dust and dirt and moisture from the outside.
According to the fourth aspect of the invention, leakage of grease held between the inner ring and the outer ring to the outside can be effectively suppressed.
According to the fifth aspect of the invention, it is possible to provide a sealed rolling bearing having the seal according to any one of the first to fourth aspects.

1 is a partial cross-sectional view of a rolling bearing according to one embodiment of the present invention; FIG. FIG. 2 is a cross-sectional view showing an enlarged seal of the rolling bearing of FIG. 1; FIG. 3 is an enlarged cross-sectional view showing a seal portion, which is a main part of the seal in FIG. 2 ; FIG. 4 is an explanatory view showing inclination angles of a main lip and an auxiliary lip of the seal portion of FIG. 3; FIG. 4 is an enlarged cross-sectional view showing a main part of a seal attached to comparative examples 1 to 3 used in a torque measurement test and a dust test of the rolling bearing of the present embodiment; 1 is a schematic diagram of a testing apparatus used for a torque measurement test of a rolling bearing according to this embodiment; FIG. It is a chart showing the result of the torque measurement test of the rolling bearing of this embodiment. 4 is a chart showing the results of a dust test of the rolling bearing of the present embodiment; FIG. 5 is a partial cross-sectional view of a rolling bearing according to another embodiment of the invention;

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described in detail based on the drawings.
As for the rolling bearing according to the present embodiment, a small size ball bearing with an outer diameter of about 10 mm used for motors incorporated in information communication equipment such as personal computers, home electric appliances, automobile control motors, blowers, fan motors, etc. is used. Although illustrated and described, seals and rolling bearings according to the present invention are not limited to such applications and dimensions.

FIG. 1 is a partial cross-sectional view of a rolling bearing 1 according to this embodiment. In the following description, the direction of the rotation axis X of the rolling bearing 1 shown in FIG. 1 is called the axial direction, and the direction perpendicular to this axial direction is called the radial direction. As shown in FIG. 1, a rolling bearing 1 according to the present embodiment is a sealed ball bearing comprising an inner ring 2, an outer ring 3, a raceway surface 2B formed on an outer peripheral surface 2A of the inner ring 2, and an outer ring 3. A plurality of rolling elements 4 (steel balls) accommodated between the inner peripheral surface 3A and the raceway surface 3B, and a retainer 5 that holds the rolling elements 4 at predetermined intervals on the raceway surfaces 2B and 3B. and have. Annular rolling bearing seals 6 , 6 (hereinafter simply referred to as seals) for sealing an annular space S between the inner ring 2 and the outer ring 3 are fixed to the outer ring 3 at both ends in the axial direction of the rolling bearing 1 . It is provided. The annular space S holds an appropriate amount of grease.

The outer peripheral surface 2A of the inner ring 2 is a cylindrical surface having a constant diameter except for the raceway surface 2B at the central portion in the axial direction. Annular seal grooves 8, 8 to which seals 6, 6 are attached are formed along the circumferential direction at both ends in the axial direction of the inner peripheral surface 3A of the outer ring 3. As shown in FIG. The seal groove 8 has a stepped shape having an axially inner small diameter portion 8A and an outer large diameter portion 8B, and the outer side wall of the large diameter portion 8B is an inclined tapered portion 8C. Inner peripheral edge portions 3C at both ends of the outer ring 3, that is, axially outer portions of the seal grooves 8, 8, have a larger diameter than the inner peripheral surface 3A. Since the seals 6, 6 provided at both ends of the rolling bearing 1 have the same structure, only one (the seal 6 on the right side in FIG. 1) will be described in detail below.

Referring to FIG. 2, the seal 6 is composed of a metal core 10 and a rubber elastic member 11 covering at least a portion of the core 10 .
The cored bar 10 is an annular member radially extending between the outer peripheral surface 2A of the inner ring 2 and the inner peripheral surface 3A of the outer ring 3 . The inner peripheral portion of the cored bar 10 extends close to the outer peripheral surface 2A of the inner ring 2, and the outer peripheral portion extends to a position substantially reaching the inner peripheral surface 3A of the outer ring 3. As shown in FIG. The outer peripheral portion of the cored bar 10 is bent at right angles toward the inner side of the rolling bearing 1 to form a cylindrical portion 10A along the inner peripheral surface 3A of the outer ring 3 . The cored bar 10 is inserted into the elastic member 11 and covered with the elastic member 11, but the region from the inner peripheral surface of the cylindrical portion 10 to the vicinity of the inner peripheral portion of the end face facing the inside of the rolling bearing 1 is is exposed to the outside. The core metal 10 reinforces the elastic member 11 and holds the shape of the seal 6 against external force.

The elastic member 11 of the seal 6 covers the outer peripheral side of the cored bar 10 and is fitted into the seal groove 8 of the outer ring 3 to be fixed to the outer ring 3 . is an annular member integrally formed with a seal portion 13 on the inner peripheral side of which a portion (main lip 16 described later) contacts the outer peripheral surface 2A of the inner ring 2 and an intermediate portion 14 therebetween. The fitting portion 12 includes a stepped portion 12A fitted to the small diameter portion 8A and the large diameter portion 8B of the seal groove 8 of the outer ring 3, an inclined portion 12B fitted to the tapered portion 8C, the stepped portion 12A and the inclined portion 12B. It has an inclined surface 12</b>C formed between and fits into the inner surface of the seal groove 8 to fix the seal 6 to the outer ring 3 . The intermediate portion 14 covers the outer side of the cored bar 10 in the axial direction and continues to the fitting portion 12 and the seal portion 13 .

Next, the seal portion 13 of the elastic member 11 will be described with reference to FIGS. 3 and 4. FIG.
The seal portion 13 is formed so as to cover the axially inner surface and the outer surface of the inner peripheral portion of the cored bar 10 and face the outer peripheral surface 2A of the inner ring 2 . The seal portion 13 has a thick portion 13A that is thicker than the portion covering the outer surface of the cored bar 10 in the axial direction and covers the inner surface of the inner peripheral portion of the cored bar 10 in the axial direction. The outer peripheral surface of the thick portion 13A forms a tapered surface 13B having a larger diameter on the metal core 10 side. An auxiliary lip 15 and a main lip 16 projecting toward the outer peripheral surface 2A of the inner ring 2 are formed on the inner peripheral portion of the seal portion 13 on the axially outer and inner sides, respectively. , an inner peripheral groove 17 facing the outer peripheral surface 2A of the inner ring 2 is formed.

The tip of the auxiliary lip 15 is out of contact with the outer peripheral surface 2A of the inner ring 2 with a slight gap H therebetween. On the other hand, the tip of the main lip 16 is in contact with the outer peripheral surface 2A of the inner ring 2 with a predetermined interference. The distal end portions of the auxiliary lip 15 and the main lip 16 are formed in a V-shape in cross section, with the axially inner and outer sides being inclined. The tip of the auxiliary lip 15 is arranged radially inside the core metal 10 , that is, at a position overlapping the core metal 10 in the axial direction. The tip of the main lip 16 is formed axially inward of the core metal 10, that is, radially inward of the thick portion 13A.

As shown in FIG. 4A, the inclination angle α1 between the axially outer surface of the auxiliary lip 15 and the outer peripheral surface 2A of the inner ring 2 is such that the axially inner surface of the auxiliary lip 15 and the inner ring 2 is smaller than the inclination angle β1 between the outer peripheral surface 2A of the As shown in FIG. 4B, the inclination angle β2 between the axially inner surface of the main lip 16 and the outer peripheral surface 2A of the inner ring 2 is the same as the axially outer surface of the main lip 16 and the inner ring 2 is smaller than the inclination angle α2 between the outer peripheral surface 2A of the

As shown in FIG. 3, an annular groove 18 is formed between the thick portion 13A of the seal portion 13 and the main lip 16. As shown in FIG. The annular groove 18 is arranged radially inward of the core metal 10 of the seal portion 13 , opens axially inward of the seal portion 13 , and extends to a depth reaching the radially inner peripheral side of the core metal 10 . The annular groove 18 has tapered side walls and narrows toward the bottom. A thin flexible portion 19 extending axially inward from the auxiliary lip 15 side is formed at the base of the main lip 16 by the inner peripheral groove 17 and the annular groove 18 between the auxiliary lip 15 and the main lip 16 . there is This flexible portion 19 is a thin portion that is included in the base of the main lip 16 and is thinner than the thickness from the annular groove 18 to the tip of the main lip 16 in the radial direction. In the illustrated example, the main lip 16 extends to a position coinciding with the inner end surface of the thick portion 13A in the axial direction. good.

In this way, in the main lip 16 extending axially inward from the main body portion of the seal portion 13 , the distal end portion connected to the main body portion of the seal portion 13 via the flexible portion 19 forms a flat outer peripheral surface 2</b>A of the inner ring 2 . is in contact with the radial direction. According to the seal 6 having such a structure, the contact pressure with the inner ring 2 can be reduced, the sliding resistance can be reduced, and the rotational torque of the inner ring 2 can be reduced.

Although the corners of the cross-sectional shape of the elastic member 11 of the illustrated seal 6 are not chamfered or rounded (R), these corners may be chamfered or rounded (R) as appropriate. may be attached.

Next, the operation of the rolling bearing 1 according to this embodiment configured as described above will be described.
The rolling bearing 1 supports the inner ring 2 and the outer ring 3 so as to be relatively rotatable, and the rolling elements 4 roll to reduce rotational resistance (rotational torque). The annular space S between the inner ring 2 and the outer ring 3 is sealed by the seals 6, 6 to prevent foreign matter such as dirt and dust and moisture from entering the annular space S from the outside. To prevent the retained grease from leaking to the outside.

At this time, the seal 6 prevents foreign matter from entering from the outside and reduces the external pressure acting on the main lip 16 by the auxiliary lip 15 which is not in contact with the inner ring 2 with a slight gap H. As shown in FIG. 4A, the auxiliary lip 15 is arranged such that the inclination angle α1 between the axially outer surface and the outer peripheral surface 2A of the inner ring 2 is equal to the inclination angle α1 between the axially inner surface and the outer peripheral surface 2A of the inner ring 2. By making the inclination angle smaller than β1 between , foreign matter and liquid tend to stay on the outer side where the inclination angle is small (α1 < β1), and foreign matter such as dust and dirt and moisture can be effectively prevented from entering from the outside. can be suppressed to Further, since the auxiliary lip 15 is arranged radially inward of the core metal 10 and the core metal 10 extends to the vicinity of the auxiliary lip 15, the rigidity is enhanced by the core metal 10 to obtain stable sealing performance. can be done.

On the other hand, the main lip 16 is provided on the thick portion 13A side, but an annular groove 18 is provided between the thick portion 13A and a thin flexible portion 19 is formed at the base of the main lip 16. As a result, the contact pressure with the inner ring 2 can be reduced, the sliding resistance can be reduced, and the rotational torque of the inner ring 2 can be reduced. At this time, as described above, the auxiliary lip 15 prevents entry of foreign matter such as dirt and dust and moisture from the outside and reduces the external pressure acting on the main lip 16. The necessary sealing performance can be secured by As shown in FIG. 4B, the main lip 16 is such that the inclination angle β2 between the axially inner surface and the outer peripheral surface 2A of the inner ring 2 is equal to the angle of inclination β2 between the axially outer surface and the outer peripheral surface 2A of the inner ring 2. By making the inclination angle smaller than α2 between , liquid and the like tend to stay on the inner side where the inclination angle is small (β2<α2), so leakage of the grease held in the annular space S is effectively suppressed. can do.

The main lip 16 has increased flexibility by forming an annular groove 18 between it and the thick portion 13A to form a thin flexible portion 19. Since the overall rigidity of the seal 6 is increased by the thickened portion 13A, stable sealing performance can be maintained. Further, since the thick portion 13A is provided continuously with the annular groove 18, the amount of deflection of the main lip 16 is regulated by the thick portion 13A, thereby preventing the main lip 16 from being turned up, and It is possible to prevent the grease inside from excessively adhering to the main lip 16. - 特許庁Further, when the rolling bearing 1 is small with an outer diameter of about 10 mm, the plate thickness of the core metal 10 and the wall thickness of the elastic member 11 are considerably thin. By providing the core metal 10 and the elastic member 11, the bondability can be ensured, so that the seal 6 can be easily manufactured by press molding or the like.

Next, the torque was performed to compare the seal performance between the rolling bearing 1 of the above embodiment and the rolling bearings (comparative examples 1 to 3) each equipped with the seals shown in FIGS. A measurement test and a dust test will be described. The seals 20A to 20C shown in FIGS. 5A to 5C differ from the seal 6 of the present embodiment only in the shape of the inner peripheral portion. The same reference numerals are used and the description of the same parts is omitted.

A seal 20A shown in FIG. 5(A) is a standard type that is mounted on a rolling bearing. is formed, and has a cross-sectional shape that is convexly curved inward in the axial direction. The seal portion 22 has only a single main lip 24 that contacts the outer peripheral surface 2A of the inner ring 2 and does not have the auxiliary lip 15 . The axial contact width of the main lip 24 with the outer peripheral surface 2A of the inner ring 2 is larger than that of the main lip 16 of the seal 6 of the present embodiment. Also, the distance between the inner peripheral edge portion of the cored bar 10 and the outer peripheral surface 2A of the inner ring 2 is slightly larger than that of the seal 6 of this embodiment. A rolling bearing having seals 20A shown in FIG.

Unlike the seal 6 of this embodiment, the seal 20B shown in FIG. does not have a thin flexible portion 19. A rolling bearing having seals 20B shown in FIG.

In a seal 20C shown in FIG. 5(C), unlike the seal 6 of the present embodiment, the thick portion 13A of the seal portion 13 does not have the annular groove 18 on the inner side in the axial direction. An annular groove 25 is formed axially outwardly of the . Therefore, the main lip 16 that contacts the outer peripheral surface 2A of the inner ring 2 does not have a thin flexible portion 19, and instead the auxiliary lip 15 that does not contact the outer peripheral surface 2A of the inner ring 2 is a thin flexible portion. 26. A rolling bearing having seals 20C shown in FIG.

The rolling bearing 1 of the present embodiment and Comparative Examples 1 to 3 are all deep groove ball bearings having an inner diameter of 3 mm and an outer diameter of 8 mm. did

(1) Torque measurement test Using the measuring device shown in FIG. 6, the rotational torque of each bearing is measured for rolling bearing 1 and Comparative Examples 1 to 3 using the measuring device M shown in FIG. As shown in FIG. 6, in the measuring device M, a set of two bearings W to be tested is inserted and fitted into the outer ring of each bearing W to the inner circumference of both ends of a cylindrical housing H, and the drive motor drives The shaft S to be rotationally driven is inserted and fitted into the inner ring, and the shaft S is rotated at 10000 rpm in a state in which a preload Fa of F=2N is applied to the inner ring. Then, the tangential force acting on the housing H attached to the outer ring is measured by a measuring device R using a load cell, and the rotational torque for each two bearings is calculated based on the measured tangential force. The calculated rotational torque for two bearings is divided by 2 to obtain the rotational torque for one bearing. The rotational torque was measured in a normal temperature and humidity environment, and the average value of 10 measurements for each bearing was calculated. It is desirable to be lower than the rotational torque of Comparative Example 1, that is, lower than 100.
FIG. 7 shows the measurement results of the rotational torque.

(2) Dust Test In the dust test, the rolling bearing 1 of the present embodiment and Comparative Examples 1 to 3 were each suspended by a thread in a desiccator, and dust was circulated in the desiccator by a fan motor for 1 hour. As the dust, JIS test powder 1 (class 8 Kanto loam) according to JIS Z 8901 is used. The anderon values before and after the dust test are measured with an anderon meter, and acoustic evaluation is performed based on the amount of increase in the anderon value before and after the dust test. At this time, the smaller the increase in the Anderon value, the smaller the extent to which the dust causes the race surface to become rougher. Acoustic evaluations for dust tests are performed in the M-band (300-1800 Hz) and H-band (1800-10000 Hz). The results of the dust test are shown in FIG.

The results of the torque measurement test shown in FIG. 7 and the results of the dust test shown in FIG. 8 reveal the following. The rolling bearing 1 of the present embodiment has a lower rotational torque and a smaller increase in the Anderon value (smaller amount of dust entering) than Comparative Example 1 (standard product). In Comparative Example 2, the amount of increase in the Anderon value is lower than in Comparative Example 1 (smaller amount of dust entering), but the rotational torque is higher. Comparative Example 3 has lower rotational torque than Comparative Example 1, but the amount of increase in the Anderon value is large (more dust enters).

In the rolling bearing 1 of the present embodiment, the annular groove 18 is provided between the main lip 16 and the thick portion 13A to form the flexible portion 19, so that the main lip 16 is contact pressure can be lowered to reduce the sliding resistance. Therefore, the rotational torque can be kept low. Further, unlike the seal 20C of Comparative Example 3, there is no annular groove 25 on the side of the auxiliary lip 15, so that the rigidity of the auxiliary lip is ensured and dust can be prevented from entering.

In the above embodiment, the case where the seal 6 is fixed to the outer ring 3 has been described, but the present invention is not limited to this, and as shown in FIG. can be applied as well. In this case, the inner ring 2 is provided with a seal groove 8 to which the seal 6 is fixed, the inner peripheral surface 3A of the outer ring 3 is formed as a cylindrical surface, the seal 6 has the fitting portion 12 formed on the inner peripheral side, and the seal portion 13. Formed on the outer peripheral side, the auxiliary lip 15 is kept out of contact with the inner peripheral surface 3A of the outer ring 3 with a minute gap, and the main lip 16 is brought into contact therewith. In FIG. 9, corresponding parts are provided with the same reference numerals as for the embodiment shown in FIGS.

Further, in the above embodiments, a ball bearing is described as an example, but the present invention is not limited to this, and can be applied to other rolling bearings such as roller bearings in the same manner. .

DESCRIPTION OF SYMBOLS 1... Rolling bearing 2... Inner ring 3... Outer ring 6... Rolling bearing seal 10... Metal core 11... Elastic member 13... Seal part 13A... Thick part 15... Auxiliary lip 16... Main lip , 18 .

Claims (6)

An annular rolling bearing seal that is fixed to the outer ring of the rolling bearing and seals between the inner ring and the outer ring,
An annular core bar extending between the inner ring and the outer ring, and an elastic member covering at least a portion of the core bar,
The elastic member has a seal portion that covers the inner surface and the outer surface of the rolling bearing in the axial direction of the inner peripheral portion of the core bar,
The seal portion has a thick portion that is thicker than a portion covering the outer surface of the core bar and covers the inner surface of the core bar,
An auxiliary lip that is not in contact with the outer peripheral surface of the inner ring with a gap and a main lip that contacts the outer peripheral surface of the inner ring axially inwardly of the auxiliary lip are formed on the inner peripheral portion of the seal portion. is,
An annular groove opening axially inward is provided between the thick portion of the seal portion and the main lip, and a thin flexible portion is formed at the base of the main lip. A tip of the main lip that contacts the outer peripheral surface of the inner ring is formed radially inward of the thick portion ,
The rolling bearing seal , wherein the thick portion is provided continuously with the annular groove at a position that regulates the amount of deflection of the main lip . An annular rolling bearing seal that is fixed to the inner ring of the rolling bearing and seals between the inner ring and the outer ring,
An annular core bar extending between the inner ring and the outer ring, and an elastic member covering at least a portion of the core bar,
The elastic member has a seal portion that covers the inner surface and the outer surface in the axial direction of the rolling bearing on the outer peripheral portion of the core bar,
The seal portion has a thick portion that is thicker than a portion covering the outer surface of the core bar and covers the inner surface of the core bar,
An auxiliary lip that is not in contact with the inner peripheral surface of the outer ring with a gap and a main lip that contacts the inner peripheral surface of the outer ring axially inwardly of the auxiliary lip is formed on the outer peripheral portion of the seal portion. formed,
An annular groove opening axially inward is provided between the thick portion of the seal portion and the main lip, and a thin flexible portion is formed at the base of the main lip. A tip of the main lip that contacts the inner peripheral surface of the outer ring is formed radially outward of the thick portion ,
The rolling bearing seal , wherein the thick portion is provided continuously with the annular groove at a position that regulates the amount of deflection of the main lip . 3. The rolling bearing seal according to claim 1, wherein the distal end of the auxiliary lip is arranged at a position where the position in the axial direction overlaps with the core bar. The inclination angle between the outer surface of the tip of the auxiliary lip in the axial direction of the rolling bearing and the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring with which the auxiliary lip is not in contact with a gap is smaller than the inclination angle between the axially inner surface of the rolling bearing at the tip of the auxiliary lip and the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring with which the auxiliary lip portion is not in contact with a gap; The rolling bearing seal according to any one of claims 1 to 3 , characterized in that: The inclination angle between the inner surface of the tip of the main lip in the axial direction of the rolling bearing and the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring with which the main lip is in contact is the angle of inclination of the main lip. The inclination angle between the outer surface of the rolling bearing in the axial direction of the tip portion and the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring with which the main lip portion contacts is smaller than the inclination angle. Item 5. The rolling bearing seal according to any one of items 1 to 4 . A rolling bearing comprising the rolling bearing seal according to any one of claims 1 to 5 .

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