JP2001140907A - Rolling bearing with sealing plate - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enhance the sealing property of a sealing plate incorporated into a rolling bearing. SOLUTION: An angle formed between an inclined side face 20 constituting the end edge 12b of a seal lip 11c and the side wall surface 15 of a seal groove 13 is regulated to inhibit elastic deformation of the seal lip 11c which may lead to a lesser sealing property. An angle formed between an inner peripheral surface 22 and the bottom surface 21 of the seal groove 13 is regulated to prevent foreign objects from the external from collecting within the seal groove 13. A curved surface portion 23 is brought into sliding contact with the side wall surface 15 to stabilize the state of contact of the seal lip 11c.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling bearing with a sealing plate, and more particularly to an improvement in a rolling bearing with a sealing plate incorporated in a rotary support portion of various types of mechanical devices.

[0002]

2. Description of the Related Art FIGS.
As shown in FIG. 8, a rolling bearing 1 with a sealing plate is used.
The rolling bearing 1 with a sealing plate has an inner race 3 having an inner raceway 2 on an outer peripheral surface and an outer raceway 4 on an inner peripheral surface.
And an outer ring 5 arranged concentrically with the inner ring raceway 2 and the outer ring raceway 4. The plurality of rolling elements 6 are rotatably held by a retainer (not shown). In addition, locking grooves 7 formed on the inner peripheral surfaces of both ends of the outer ring 5 over the entire circumference are respectively provided.
The outer peripheral edge of the sealing plate 8 is locked.

Each of the sealing plates 8 is formed in a ring shape by reinforcing a resilient material 10 such as an elastomer such as rubber with a metal core 9 formed of a metal plate such as a steel plate in a ring shape. Consisting of The outer peripheral edge of the elastic member 10 protrudes slightly outward in the diameter direction (the vertical direction in FIGS. 7 to 8) than the outer peripheral edge of the cored bar 9. It is locked. On the other hand, the inner peripheral edge of the elastic member 10 projects sufficiently inward in the diameter direction from the inner peripheral edge of the cored bar 9 to form a seal lip 11. Then, the edge 12 of the seal lip 11 is attached to the inner ring 3.
Of the pair of side wall surfaces 14 and 15 forming the seal grooves 13 formed on the outer peripheral surfaces of both ends of the pair of the inner peripheral surfaces, the inner wall surface 15 is slidably contacted with the inner side wall surface 15 in the axial direction (the left-right direction in FIGS. 7 and 8). In the illustrated example, the elastic member 10 in a free state is indicated by a solid line, and a state in which the seal lip 11 abuts on the side wall surface 15 and is elastically deformed is indicated by a chain line.

In the rolling bearing 1 with a sealing plate configured as described above, the relative position between the member in which the inner ring 3 is externally fixed and the member in which the outer ring 5 is internally fixed is determined based on the rolling of the rolling elements 6. Allow rotation. Further, a pair of sealing plates 8 whose outer peripheral edges are locked to the inner peripheral surfaces of both ends of the outer ring 5 prevent the grease filled in the space 16 in which the rolling elements 6 are installed from leaking outside. In addition, foreign substances such as dust and water floating outside are prevented from entering the space 16 in which the rolling elements 6 are installed.

[0005] In the above-described rolling bearing 1 with a sealing plate, grease leakage may occur in the following manner. That is, when the rolling elements 6 roll, the grease adhering to the rolling elements 6 is scraped off on the inner diameter side of the retainer, and a part of the grease is pushed out to the seal groove 13 side. And with this extruded grease,
The sealing lip 11 of each of the sealing plates 8 is
Is elastically deformed in a direction away from the side wall surface 15 to form a minute gap between the seal lip 11 and the side wall surface 15, and grease leaks through the minute gap. In addition, when the pressure in the space 16 in which the rolling elements 6 are installed increases due to rolling friction or temperature rise due to agitation resistance of the grease during use, the elastic deformation of the seal lip 11 further increases, and grease leakage is further reduced. It becomes remarkable.

In order to prevent the grease from leaking due to such a cause, it has been attempted to improve the sealing performance by devising a structure of a sealing plate or the like. For example, FIG.
26 shows a rolling bearing 1a with a sealing plate described in Japanese Patent No. 26449. The sealing plate 8a to be incorporated into the rolling bearing 1a with a sealing plate includes an edge 12a of a sealing lip 11a forming an inner peripheral edge of the elastic member 10a and the sealing lip 11a.
a regulates the angle formed by the side wall surface 15 of the seal groove 13 with which the sliding groove a contacts. Specifically, one of the pair of inclined side surfaces 17 and 18 forming the edge portion 12a has one inclined side surface 17.
The angle theta ₁₇ between the side walls 15 and 50 to 85 degrees, thereby improving the sealing property at the angle theta ₁₈ with the other inclined side surface 18 and the side wall surface 15 can be 5 to 40 degrees and I have. Further, a constricted portion 19 is provided on the inner peripheral edge portion of the elastic member 10a over the entire periphery to improve the followability of the seal lip 11a with the side wall surface 15.

As shown in FIG. 10, a seal lip 1 constituting an inner peripheral edge of an elastic member 10b constituting a sealing plate 8b.
1b is bifurcated, and the seal lip 11b is positioned at two axially separated positions on the outer peripheral surface of the end of the inner ring 3 so as to straddle the seal groove 13 formed on the outer peripheral surface of the end of the inner race 3. A structure in which sliding contact is performed over the entire circumference is also conventionally known. Further, although not shown, Japanese Patent Application Laid-Open No. 7-2
93571 and JP-A-7-139553,
The seal lip forming the inner peripheral edge portion of the elastic material is slidably contacted with the axially outer side wall surface of the pair of side wall surfaces forming the seal groove, and the diametric length and the axial thickness of the seal lip are regulated. By doing so, a structure for ensuring a sealing property is described. Furthermore, Japanese Utility Model Publication No. 6-27859 discloses that
Similarly, there is described a structure in which a seal lip is slidably contacted with an axially outer side wall surface and a variable labyrinth gap is formed by another seal lip which is displaced by centrifugal force, thereby ensuring sealability.

[0008]

In the case of the conventionally known rolling bearings 1 and 1a with a sealing plate which are constructed and operate as described above, there are the following points to be solved. First, FIG.
8, the angle between the edge 12 of the seal lip 11 and the side wall surface 15 of the seal groove 13 is small. That is, the side wall surface 15 and the side wall surface 15
The angle α formed between the edge portion 12 and the inclined side surface 20 facing the edge portion 12 is small. For this reason, when grease is pushed out to the seal groove 13 side and enters between the side wall surface 15 and the inclined side surface 20, a wedge action accompanying the entry of the grease works, and the seal lip 11 is moved from the side wall surface 15 from the side wall surface 15. It is easy to be elastically deformed in the direction away from it, and a minute gap is easily generated between the seal lip 11 and the side wall surface 15. In addition, the edge portion 12 of the seal lip 11 and the sliding contact portion between the seal groove 13 are likely to make surface contact, and it is difficult to maintain a stable contact state.

Further, Japanese Patent Application Laid-Open No. 8-226449 shown in FIG.
In the case of the structure described in the official gazette, since the constricted portion 19 is provided at the inner peripheral edge of the elastic member 10a, the seal lip 11a is provided.
Are easily deformed elastically, and a minute gap is easily generated between the seal lip 11a and the side wall surface 15. Also, this seal lip 11
Since the angle θ ₁₇ formed between the one inclined side surface 17 forming the edge 12 a of FIG. 1a and the side wall surface 15 of the seal groove 13 is increased, the axial dimension of the entire sealing plate 8 b increases. Further, the other inclined side surface 18 constituting the edge portion 12a is formed.
Foreign matter easily accumulates between the side wall surface 15 and
In addition, the accumulated foreign matter pushes the seal lip 11a away from the side wall surface 15. Because of this,
In particular, when the outer ring is used for rotation, it is difficult to prevent the foreign matter from entering.

In the case of the structure shown in FIG. 10, the inner ring 3 is formed on the basis of the shape and dimensional error of the seal groove 13 and the displacement between the center axes of the inner ring 3 and the outer ring 5 due to external force applied during use. The contact state of the sliding contact portion between the outer peripheral surface of the end portion and the leading edge of the seal lip 11b is likely to vary, and it is difficult to obtain stable sealing performance.

Further, in the case of the structures described in JP-A-7-293571 and JP-A-7-139553, the seal lip is slidably contacted with the axially outer side wall surface to release the pressure in the internal space. It is necessary to provide an air hole of
Grease easily leaks from these air holes. In addition,
In the case of the structure described in Japanese Patent No. 27859, the seal lip forming the labyrinth gap is easily hardened due to thermal deterioration or the like, and the flexibility of the grease slip cannot be sufficiently secured for a long time. It is difficult to maintain good sealing properties over a long period of time. The rolling bearing with a sealing plate of the present invention has been invented to solve any of the above-mentioned disadvantages.

[0012]

The rolling bearing with a sealing plate according to the present invention has the same structure as the above-mentioned conventional rolling bearing with a sealing plate.
An inner ring having an inner raceway on the outer peripheral surface, an outer race having an outer raceway on the inner peripheral surface, a plurality of rolling elements provided rotatably between the inner raceway and the outer raceway; And a sealing plate whose outer peripheral edge is engaged with an engaging groove formed on the inner peripheral surface of the end of the outer ring over the entire circumference. Then, the edge of the elastic material constituting the inner peripheral edge of the sealing plate is brought into sliding contact with the side wall surface of a seal groove formed on the outer peripheral surface of the end of the inner ring. In particular, in the rolling bearing with a sealing plate of the present invention, the edge portion of the elastic material has an inclined side surface facing the side wall surface of the seal groove, and is located diametrically inward from the inclined side surface. An inner peripheral surface facing the bottom surface of the seal groove, and a continuous portion that connects the inclined side surface and the inner peripheral surface are provided. Then, the continuous portion is slidably contacted with the side wall surface of the seal groove, and the angle formed between the side wall surface and the inclined side surface in a state where the continuous portion is in contact with the side wall surface is 10 to 45 degrees ( (Preferably 30 to 40 degrees), and the bottom surface of the seal groove and the inner peripheral surface are inclined relatively to each other in a direction parallel or closer to the axially outer end surface side of the inner ring so as to be closer to the outer surface. The angle formed with the inner peripheral surface is set to 0 to 30 degrees (preferably, 10 to 20 degrees). Preferably, the continuous portion is a curved portion having a circular cross section. In addition, L is the axial interference between the edge of the elastic material and the sidewall of the seal groove, and P is the force that presses the edge against the sidewall based on the rigidity of the sealing plate. In this case, the P / L is set to 2.9 to 9.8 N / mm (300 to 1000 gf / mm), and the interference L is set to 1 to the diameter of the ball as the rolling element.
3%.

[0013]

In the case of the rolling bearing with a sealing plate of the present invention constructed as described above, the angle between the side wall surface of the seal groove and the inclined side surface facing this side wall surface is 10 to 45 degrees, more preferably 30 to 45 degrees. Since the angle is restricted to 40 degrees, even if the grease is pushed out to the seal groove side, the elastic material is hardly elastically deformed by the wedge action, and a minute gap is hardly generated between the elastic material and the side wall surface. When the angle is less than 10 degrees, the minute gap is easily generated due to a wedge effect generated when grease is pushed out to the seal groove side. On the other hand, when the angle exceeds 45 degrees, the rigidity of the portion where the inclined side surface is formed at the edge of the elastic member is reduced.
In other words, when the grease is pushed out to the seal groove side, the force for pushing the inclined side surface by the grease increases, so that the minute gap also tends to occur. Therefore, the angle is restricted to a range of 10 to 45 degrees. If the angle is in the range of 30 to 40 degrees, the occurrence of the minute gap can be more effectively prevented.

The bottom face of the seal groove and the bottom face of the seal groove are relatively opposed to each other in a direction in which the distance between the bottom face of the seal groove and the inner peripheral face becomes parallel or becomes larger toward the outer end face side in the axial direction of the inner ring. To make an angle of 0 to 30 degrees, more preferably 10 to 20 degrees.
Foreign matter that has entered the seal groove from the outside and has come into contact with the inner peripheral surface does not push the edge of the elastic material away from the side wall surface. If the inclination direction is reversed, the edge of the elastic material tends to separate from the side wall surface due to the foreign matter that has entered the seal groove, and there is a possibility that the sealing property is reduced. Even if the inclination direction is as described above, if the angle formed between the bottom surface of the seal groove and the inner peripheral surface opposed to the bottom surface exceeds 30 degrees, the edge of the elastic material will The thickness of the portion in sliding contact with the side wall surface is reduced, the rigidity of this portion is reduced, and it is difficult to secure the surface pressure of the sliding contact portion between the edge portion and the side wall surface, and it is also difficult to secure sufficient sealing performance. Become. Therefore, the inclination direction and the inclination angle between the bottom surface and the inner peripheral surface of the seal groove,
Regulated as described above. If the inclination angle is in the range of 10 to 20 degrees, the above-mentioned sealing performance can be more effectively ensured.

If the continuous portion that connects the inclined side surface and the inner peripheral surface is a curved surface portion having an arc-shaped cross section, the sliding contact between the continuous portion and the side wall surface of the seal groove can be stabilized. Better sealing performance can be ensured. Further, when the axial interference between the edge portion of the elastic material and the side wall surface of the seal groove is L, and the force for pressing the edge portion against the side wall surface based on the rigidity of the sealing plate is P. In addition, P / L is 2.9-9.8N /
mm (300 to 1000 gf / mm), and when the above-mentioned interference L is 1 to 3% of the diameter of the ball as the rolling element, the elastic deformation of the elastic material, which leads to a decrease in the sealing property, is less likely to occur. Further, sealing properties can be ensured. If the P / L is less than 2.9 N / mm and the interference L is less than 1%, the contact pressure at the sliding contact portion between the continuous portion and the side wall surface is too low, and sufficient sealing properties are obtained. It becomes difficult. Also, the above P / L is 2.9.
If it is less than N / mm and the above-mentioned interference L exceeds 3%, the rigidity of the sealing plate is too low, the fluctuation of the outer peripheral edge of the sealing plate becomes large, and it becomes difficult to obtain a stable sealing property. Conversely, when the P / L exceeds 9.8 N / mm and the interference L is 1%
If it is less than 7, the rigidity of the sealing plate is too high, and the contact pressure fluctuates greatly even with a slight displacement, and it is also difficult to obtain a stable sealing property. On the other hand, when the P / L exceeds 9.8 N / mm and the interference L exceeds 3%, the contact pressure of the sliding contact portion becomes excessive, and the rotational torque of the rolling bearing with a sealing plate is reduced. Because of the large size, the continuous portion wears out, and it becomes impossible to secure the sealing performance for a long period of time.

[0016]

1 and 2 show a first embodiment of the present invention. The feature of the present invention is that the sealing plate 8 is provided.
The point is that the shape of the seal lip 11c that forms the inner peripheral edge of the elastic member 10c that forms the sealing plate 8c has been devised in order to improve the sealing performance of the sealing plate 8c. The basic configuration itself of the rolling bearing 1b with a sealing plate is the same as the conventional structure shown in FIGS. 7 and 8 above, and therefore, the description of the equivalent parts is omitted or simplified. The following description focuses on the differences from the first embodiment.

In the sealing plate 8c of the rolling bearing 1b with a sealing plate of the present invention, the cross-sectional shape of the edge 12b of the sealing lip 11c is determined by changing the cross-sectional shape of the pair of side walls 14, 15 forming the sealing groove 13. The side wall surface 15 on the inner side in the axial direction (the left-right direction in FIG. 1) has a substantially V-shape in which a convex surface having an arc-shaped cross section is formed. That is, the edge 12b of the elastic member 10c is
An inclined side surface 20 facing the side wall surface 15 and inclined in a direction away from the side wall surface 15 as going diametrically outward.
And a cylindrical inner peripheral surface 22 in a free state, which is located diametrically inward from the inclined side surface 20 and faces the bottom surface 21 of the seal groove 13, and connects the inclined side surface 20 and the inner peripheral surface 22 continuously. And a curved surface portion 23 having an arc-shaped cross section.

In a state where the outer peripheral edge of the sealing plate 8c having the above-described sealing lip 11c is locked in the locking groove 7 of the outer ring 5, as shown by a chain line in FIG.
The curved surface portion 23 comes into sliding contact with the side wall surface 15 of the seal groove 13 in a state where 1 c is elastically deformed outward in the axial direction of the inner ring 3. When the curved surface portion 23 is in sliding contact with the side wall surface 15 as described above, the angle α between the side wall surface 15 and the inclined side surface 20 is 10 to 45 degrees, and more preferably 30 to 40 degrees. The bottom surface 21 of the seal groove 13 and the inner peripheral surface 22
Are parallel or on the axially outer end face side of the inner ring 3 (FIG. 1).
2 (left side of ２2), the interval is relatively inclined in such a direction that the interval becomes larger. Then, the bottom surface 21 of the seal groove 13
And the inner peripheral surface 22 have an angle β of 0 to 30 degrees, and more preferably 10 to 20 degrees.

Further, the edge 1 of the seal lip 11c
The axial interference (the amount of elastic deformation) L between 2b and the side wall surface 15 of the seal groove 13 is set to 1 to 1 of the diameter of the ball that is the rolling element 6.
3%. When the force for pressing the edge 12b against the side wall surface 15 obtained by the interference L based on the rigidity of the sealing plate 8c is P / L.
Is regulated to 2.9 to 9.8 N / mm (300 to 1000 gf / mm). A labyrinth seal is formed inside the seal lip 11c so as to be close to and opposing a part of the surface of the inner ring 3, and a grease slip 24 for suppressing the amount of grease reaching the seal lip 11c is provided. . In addition, a labyrinth seal is formed outside the seal lip 11c so as to be closely opposed to the outer peripheral surface of the inner ring 3 at a portion outside the seal groove 13 so as to suppress the amount of foreign matter entering the seal groove 13. Dust lip 25 is provided.

In the case of the rolling bearing 1b with a sealing plate of the present invention constructed as described above, the angle α between the side wall surface 15 of the seal groove 13 and the inclined side surface 20 facing the side wall surface 15 is formed.
Is set to 10 to 45 degrees, more preferably 30 to 40 degrees, so that even if grease is pushed out to the seal groove 13 side from the retainer holding the rolling elements 6, elastic deformation of the seal lip 11c due to the wedge action occurs. It is difficult to form a minute gap between the seal lip 11c and the side wall surface 15. The angle α is 10 to 45 degrees, more preferably 30 to 45 degrees.
The reason for setting the angle to 40 degrees is as described above.

Also, the bottom surface of the seal groove 13 is relatively parallel to the bottom surface 21 of the seal groove 13 and the inner peripheral surface 22 in such a direction that the distance between the bottom surface 21 and the inner peripheral surface 22 becomes larger toward the outer end surface side of the inner race 3 in the axial direction. 21 and an inner peripheral surface 22 facing the bottom surface 21
Is 0 to 30 degrees, more preferably 10 to 2 degrees.
Since it is inclined so as to be 0 degrees, foreign matter that has entered the seal groove 13 from the outside and has come into contact with the inner peripheral surface 22 causes the edge 12 b of the elastic member 10 c to move toward the side wall surface 15.
It does not push away from you. The seal groove 13
The foreign matter that has entered inside is subjected to a component force in the direction of coming out of the seal groove 13 due to the contact with the inner peripheral surface 22.
Foreign matter hardly accumulates in the seal groove 13. In the illustrated example, the curved surface portion 23 having an arc-shaped cross section is slidably contacted with the side wall surface 15 of the seal groove 13, so that a stable contact state can be maintained. Furthermore, by restricting the interference L and the pressing force P of the edge portion 12b of the seal lip 11c, the elastic deformation of the seal lip 11c is more unlikely to occur, and the sealing performance is further improved. Incidentally, as a cage of the rolling bearing with a sealing plate of the present invention, for example, Japanese Patent Application No.
The use of a retainer having a structure for preventing grease from remaining on the inner diameter side, as described in JP-295823-A, makes it possible to more effectively secure the above-mentioned sealing performance.

Next, FIGS. 3 and 4 show a second example of the embodiment of the present invention. In the case of this example, the dust lip 25a provided on the outer peripheral portion of the seal lip 11d at the inner peripheral edge of the elastic member 10d constituting the sealing plate 8d is made to protrude in the axial direction from the inner peripheral portion of the outer surface of the seal lip 11d. Thus, the outer diameter side of the outer half opening of the seal groove 13 is closed. The structure and operation of the dust lip 25a are substantially the same as those of the first example except that the shape of the seal lip 11d is slightly different from that of the dust lip 25a.

[0023]

EXAMPLES Experiments performed by the present inventors to confirm the effects of the present invention will be described. In this experiment, the conventional example in which the sealing plate 8 shown in FIGS. 7 and 8 is incorporated, and the bottom 21 of the seal groove 13 and the inner periphery of the seal lip 11e, as shown in FIG. A comparative example in which a sealing plate 8e in which the surface 22a is relatively inclined in a direction in which the gap becomes smaller as approaching to the axially outer end surface side of the inner ring 3 is incorporated, and a sealing plate 8c shown in FIGS. 3 and FIGS.
Was used under the same conditions, and the leakage rate of each grease and the amount of water penetration were measured. Table 1 shows the specifications of the conventional example, the comparative example, and the products 1 and 2 of the present invention. FIG. 5 shows the result of measuring the leakage rate of the grease, and FIG. Indicated. In the experiment, the grease leakage rate was 8 for each sample of the same type, for a total of 32.
A total of 16 samples were used for each sample of the same kind with respect to the amount of water intrusion.

[0024]

[Table 1]

As is apparent from FIGS. 5 and 6 showing the results of experiments conducted under such conditions, the rolling bearing with a sealing plate of the present invention has a good effect of preventing leakage of grease and entry of foreign matter. And the durability can be improved.

[0026]

Since the rolling bearing with a sealing plate of the present invention is constructed and operates as described above, it effectively prevents leakage of grease and invasion of foreign matters, and reliability of various devices incorporating the rolling bearing with a sealing plate. In addition, it can contribute to improvement in durability.

[Brief description of the drawings]

FIG. 1 is a partial cross-sectional view showing a first example of an embodiment of the present invention.

FIG. 2 is an enlarged view of a portion A in FIG.

FIG. 3 is a partial sectional view showing a second example of the embodiment of the present invention.

FIG. 4 is an enlarged view of a portion B in FIG. 3;

FIG. 5 is a graph showing the results of an experiment performed to confirm the effect of the present invention with respect to grease leakage.

FIG. 6 is a graph showing the results of an experiment performed to confirm the effect of the present invention with respect to water intrusion.

FIG. 7 is a partial sectional view showing a first example of a conventional structure.

FIG. 8 is an enlarged view of a portion C in FIG. 7;

FIG. 9 is a partial sectional view showing a second example of the conventional structure.

FIG. 10 is a partial sectional view showing a third example of the conventional structure.

FIG. 11 is a view similar to FIG. 2, showing a comparative example used to confirm the effect of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1, 1a, 1b Rolling bearing with sealing plate 2 Inner raceway 3 Inner race 4 Outer raceway 5 Outer race 6 Rolling element 7 Locking groove 8a, 8b, 8c, 8d, 8e Sealing plate 9 Core metal 10, 10a, 10b, 10c, 10d Elasticity Material 11, 11a, 11b, 11c, 11d, 11e Seal lip 12, 12a, 12b Edge 13 Seal groove 14 Side wall surface 15 Side wall surface 16 Space 17 Inclined side surface 18 Inclined side surface 19 Constricted portion 20 Inclined side surface 21 Bottom surface 22, 22a Inner circumferential surface 23 Curved surface 24 Grease slip 25, 25a dust lip

Claims (3)

[Claims] An inner race having an inner raceway on an outer peripheral surface, an outer race having an outer raceway on an inner peripheral surface, a plurality of rolling elements rotatably provided between the inner raceway and the outer raceway; A sealing plate whose entire periphery is formed in a ring shape by reinforcing the material with a cored bar, and whose outer peripheral edge is locked over the entire circumference in a locking groove formed in the inner peripheral surface at the end of the outer ring. In the rolling bearing with a sealing plate, an edge of the elastic material constituting an inner peripheral edge of the sealing plate is brought into sliding contact with a side wall surface of a sealing groove formed on an outer peripheral surface of an end of the inner ring. The edge of the material has an inclined side surface facing the side wall surface of the seal groove, an inner peripheral surface located diametrically inward of the inclined side surface and facing the bottom surface of the seal groove, and these inclined side surfaces. A continuous portion for making the inner peripheral surface continuous with the inner circumferential surface, and when the continuous portion is slidably contacted with the side wall surface of the seal groove, In both cases, the angle formed between the side wall surface and the inclined side surface is 10 to 45 degrees in a state where the continuous portion is in contact with the side wall surface, and the bottom surface of the seal groove and the inner peripheral surface are parallel or the inner ring is formed. A rolling bearing with a sealing plate, characterized in that the angle between the bottom surface and the inner peripheral surface is set to 0 to 30 degrees by relatively inclining in such a direction that the interval becomes larger toward the outer end surface in the axial direction. 2. The rolling bearing with a sealing plate according to claim 1, wherein the continuous portion is a curved portion having a circular cross section. 3. A case in which an axial interference of an end portion of an elastic material with respect to a side wall surface of a seal groove is L, and a force for pressing the end portion against the side wall surface based on rigidity of a sealing plate is P. 3. The method according to claim 1, wherein P / L is set to 2.9 to 9.8 N / mm, and the interference L is set to 1 to 3% of a diameter of a ball as a rolling element. Rolling bearing with sealing plate.