JP7029155B2 - Sealing device - Google Patents

Description

The present invention relates to a sealing device that is press-fitted between a relatively axially rotating inner member and an outer member to seal between the inner member and the outer member.

Examples of the sealing device as described above include a sealing device in which two sealing members fitted to the inner member and the outer member are press-fitted between the inner member and the outer member in a combined state. In Patent Document 1 and Patent Document 2, a sealing device that is assumed to be press-fitted between an inner member and an outer member that rotate relatively coaxially in a state where members corresponding to the two sealing members are combined. Is described.

Jitsufuku No. 5-5342 Gazette Japanese Unexamined Patent Publication No. 5-196146

By the way, in the sealing device as described above, a labyrinth is provided at an axially opposed position between the two sealing members, and while reducing the rotational torque of the member on the rotating side, the medium to be sealed into the sealing device is provided. Measures may be taken to prevent intrusion. In this case, in a state where the two members are combined, one of the sealing members is pressed along the axial direction and press-fitted between the inner member and the outer member, whereby a predetermined value between the inner member and the outer member is determined. It is installed in the position. However, at the time of this press-fitting, the other seal member receives the press-fitting resistance, and the positional relationship between one seal member and the other seal member in the axial direction becomes close to each other. Then, even though the portion is designed to be the labyrinth, one member may be in contact with the other member. As described above, when the sealing device is press-fitted, if the portions designed to be labyrinth are in contact with each other, the effect of reducing the desired rotational torque by the labyrinth cannot be obtained.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a sealing device capable of ensuring a desired effect of reducing rotational torque after completion of press fitting between an inner member and an outer member.

The sealing device according to the present invention includes a first sealing member attached to one member of a relatively axially rotating inner member and an outer member, and a second sealing member attached to the other member of the inner member and the outer member. A sealing device that is mounted in a state of being press-fitted between the inner member and the outer member in a combined state and used to seal between the inner member and the outer member. The first seal member includes a core metal having a first cylindrical portion fitted to the one member and a first disk portion extending radially from one end of the first cylindrical portion, and the core metal. The second seal member includes the attached first seal side seal body, and the second seal member includes a second cylindrical portion fitted to the other member via a second seal side elastic portion made of an elastic material, and the said. The second sealing member includes a second disc portion that extends radially from one end of the second cylindrical portion and faces the first disc portion in the axial direction, and is in the press-fitted state. It is allowed to move along the axial direction due to the elastic strain of the elastic portion on the second seal side, and the first seal member and one of the second seal members are press-fitted in the state of being press -fitted. A reaction force generating portion that elastically contacts the other of the first sealing member and the second sealing member to generate a reaction force in a direction opposite to the press-fitting direction is provided, and the reaction force generating portion and the first 2 It is characterized in that the second seal member is separated from the first seal member in a direction opposite to the press-fitting direction by the action of the elastic portion on the seal side .

According to the sealing device of the present invention, when the second sealing member is pressed and press-fitted between the inner member and the outer member in a state where the first sealing member and the second sealing member are combined, the elasticity of the second sealing side is increased. Elastic strain occurs in the portion. Further, the reaction force generating portion provided on one of the first seal member and the second seal member elastically contacts the other of the first seal member and the second seal member. Then, when the press-fitting of the sealing device is completed and the pressing against the second sealing member is released, the elastic portion on the second sealing side in the elastically strained state springs back, and this springback springs back through the second cylindrical portion. It acts on the sealing member. As a result, the second seal member moves in a direction away from the first seal member. Further, the reaction force generated by the reaction force generating portion promotes the movement of the second seal member. Then, the reaction force generating portion is separated from the other of the first seal member and the second seal member, and is in a state of being close to the other. When the reaction force generating portion is brought close to the other of the first seal member and the second seal member in this way, a labyrinth is formed in this portion. Therefore, it is possible to secure the sealing performance as a sealing device and reduce the rotational torque due to the relative axial rotation of the inner member and the outer member. Further, by moving the second seal member in the direction away from the first seal member, the elastic strain generated in the elastic portion on the second seal side can be corrected, and the plastic flow of the elastic portion on the second seal side can be reduced. can.

In the sealing device of the present invention, the first seal side seal body is provided with a first seal side seal lip in contact with the second disk portion, and the reaction force generating portion is provided on the first seal side seal body. Even if it is formed so as to have a shorter axial length and a thicker thickness than the first seal-side seal lip, and to be in contact with the second disk portion at the time of press-fitting. good.
According to this, since the reaction force generating portion has a higher rigidity than the seal lip, a larger reaction force acts on the second disk portion than on the first seal side seal lip. Therefore, the reaction force generated by the reaction force generating portion more accurately promotes the movement of the second seal member in the direction away from the first seal member.

In the sealing device of the present invention, the first cylindrical portion of the first seal member is fitted to the one member via the first seal side elastic portion made of an elastic material, and the first seal side elastic portion of the first seal member. The thickness is larger than the thickness of the elastic portion on the second seal side, and the fitting tightening allowance of the elastic portion on the first seal side with respect to the one member is larger than the fitting tightening allowance of the elastic portion on the second seal side with respect to the other member. It may be small.
According to this, when the press-fitting is completed, the first seal member receives a springback action by the elastic portion on the first seal side and moves in the same direction as the second seal member. In this case, the size relationship between the thickness of the elastic portion on the first seal side and the fitting tightening margin and the thickness of the elastic portion on the second seal side and the fitting tightening margin is set as described above, so that the second seal member The amount of movement along the axial direction of the first seal member is larger than the amount of movement along the axial direction of the first seal member. Then, the difference in the relative movement amount between the first seal member and the second seal member is the amount of separation of the second seal member from the first seal member. Therefore, this amount of separation can be reduced as compared with the case where the springback does not act on the first seal member, and the gap between the first seal member and the second seal member of the reaction force generating portion is set to a minute state. Can be done. As a result, the sealing performance by the labyrinth is more accurately exhibited.

In the sealing device of the present invention, the second seal member may have a second seal side seal body provided with a second seal side seal lip close to the first seal member.
According to this, by further having the second seal side seal lip, it is possible to improve the sealing performance while suppressing the increase in the rotational torque.

According to the present invention, the sealing device is press-fitted between the inner member and the outer member, and the effect of reducing the desired rotational torque can be ensured after the press-fitting is completed.

It is a schematic vertical sectional view which shows an example of the bearing device to which the sealing device which concerns on this invention is applied. It is an enlarged view of the X part of FIG. 1, and is the figure which shows one Embodiment of the sealing apparatus which concerns on this invention. It is the same figure as FIG. 2 which shows the other embodiment of the sealing apparatus which concerns on this invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 shows a bearing device 1 that rotatably supports a wheel (not shown) of an automobile. This bearing device 1 is a hub bearing, and is generally composed of an outer ring (outer member) 2, a hub ring 3, an inner ring member 4 fitted and integrated on the vehicle body side of the hub ring 3, and an outer ring 2. It is configured to include two rows of rolling elements (balls) 6 ... Intersed between the hub ring 3 and the inner ring member 4. In this example, the hub ring 3 and the inner ring member 4 form the inner ring (inner member) 5. The outer ring 2 is fixed to the vehicle body (not shown) of the automobile. Further, a drive shaft 7 is coaxially spline-fitted to the hub wheel 3, and the drive shaft 7 is connected to a drive source (drive transmission unit) (not shown) via a constant velocity joint 8. The drive shaft 7 is integrated with the hub wheel 3 by a nut 70, and the hub wheel 3 is prevented from being pulled out from the drive shaft 7. The inner ring 5 (hub ring 3 and inner ring member 4) can rotate (coaxially rotate) around the axis L with respect to the outer ring 2, and an annular bearing space S is formed between the outer ring 2 and the inner ring 5. To. In the bearing space S, two rows of rolling elements 6 ... can roll the raceway rings 2a of the outer ring 2, the hub wheels 3 and the raceway rings 3a, 4a of the inner ring member 4 while being held by the retainer 6a. It is a bearing. The hub wheel 3 has a cylindrical hub wheel main body 30 and a hub flange 32 formed so as to extend radially outward from the hub wheel main body 30 via a rising base 31, and a bolt 33 is attached to the hub flange 32. And the wheels are mounted and fixed by nuts (not shown).
In the following, the side facing the wheel (the side facing the left side in FIG. 1) along the axis L direction is referred to as the wheel side, and the side facing the vehicle body (the side facing the right side) is referred to as the vehicle body side.

Bearing seals 9, 90 are mounted between the outer ring 2 and the inner ring member 4 and between the outer ring 2 and the hub ring 3 at both ends of the bearing space S along the axis L direction, and the bearing is supported. Both ends of the space S along the axis L direction are sealed. This prevents the infiltration of muddy water and the like into the bearing space S and the leakage of the lubricant (grease and the like) filled in the bearing space S to the outside.

A bearing seal (sealing device) 9 as an embodiment of the sealing device according to the present invention will be described with reference to FIG. The bearing seal 9 of the present embodiment is configured by combining a first seal member 10 attached to the outer ring (one member) 2 and a second seal member 20 attached to the inner ring (the other member) 5. The first seal member 10 and the second seal member 20 are press-fitted between the outer ring 2 and the inner ring 5 from the vehicle body side in a combined state to seal the vehicle body side end portion of the bearing device 1. The first seal member 10 has a core provided with a first disk portion 112 extending radially inward from one end portion 111a of the first cylindrical portion 111 and the first cylindrical portion 111 fitted to the inner peripheral surface 2b of the outer ring 2. The gold 11 and the first seal side seal body 12 attached to the core metal 11 are included. The first cylindrical portion 111 is fitted to the inner peripheral surface 2b of the outer ring 2 via the elastic portion 13 on the first seal side. The one end 111a of the first cylindrical portion 111 is located on the vehicle body side, while the other end 111b of the first cylindrical portion 111 is located on the wheel side.

The second seal member 20 extends radially outward from the second cylindrical portion 211 fitted to the outer peripheral surface 4b of the inner ring member 4 and the one end portion 211a of the second cylindrical portion 211, and is the first disk in the axis L direction. Includes a second disc portion 212 facing the portion 112. The second cylindrical portion 211 is fitted to the outer peripheral surface 4b of the inner ring member 4 via the second seal side elastic portion 23 made of an elastic material. The second cylindrical portion 211 and the second disk portion 212 form a slinger 21 made of a metal ring, and in the present embodiment, the slinger 21 substantially constitutes the second seal member 20. Hereinafter, in the present embodiment, the second seal member 20 may be referred to as a slinger 21. In the present embodiment, the slinger 21 further includes a third disk portion 213 extending radially outward from the other end portion 211b of the second cylindrical portion 211. The radial length of the third disk portion 213 is formed to be smaller than the radial outward extension width of the second disk portion 212. The one end portion 211a of the second cylindrical portion 211 is located on the vehicle body side, while the other end portion 211b of the second cylindrical portion 211 is located on the wheel side.

The first seal side seal body 12 is made of an elastomer such as a rubber material. The first seal side seal body 12 is fixed so as to cover the outer peripheral surface 111c of the first cylindrical portion 111 from the other end portion 111b of the first cylindrical portion 111. Further, the first seal side seal body 12 is integrally fixed to the core metal 11 so as to wrap around the inner diameter side end portion 112b from the vehicle body side surface 112a of the first disk portion 112 and reach the wheel side surface 112c. The first seal-side elastic portion 13 is configured as a part of the first-seal-side seal body 12 by a portion that covers the outer peripheral surface 111c of the first cylindrical portion 111. The first seal side seal body 12 is formed with an axial lip (first seal side seal lip) 12a that elastically contacts the first side surface 212a of the second disk portion 212. The first seal side seal body 12 is further formed with two radial lips (seal lips) 12b and 12c that are in contact with the outer peripheral surface 211c of the first cylindrical portion 211. The two radial lips 12b and 12c are formed so as to face away from each other along the axis L direction, and a garter spring 12d is elastic on the outer peripheral portion of the radial lips 12c facing the wheel side (bearing space S side). It is fitted in the target. In the portion of the seal body 12 on the first seal side that covers the first disk portion 112, the reaction force generating portion 14 is formed so as to bulge toward the second disk portion 212 side (vehicle body side). The tip surface 14a of the reaction force generating portion 14 is formed on a surface parallel to the first side surface 212a of the second disk portion 212. The reaction force generating portion 14 abuts on the first side surface 212a of the second disk portion 212 at the time of press-fitting, which will be described later, and after the press-fitting is completed, the reaction force generating portion 14 is expected to be between the first side surface 212a of the second disk portion 212. It is configured to form a labyrinth r. Further, the reaction force generating portion 14 is formed so that the length in the axial L direction is shorter than that of the axial lip 12a and is thicker than the thickness of the axial lip 12a.

The second seal-side elastic portion 23 is made of an elastomer such as a rubber material like the first-seal-side elastic portion 13, and is integrally fixed to the inner peripheral surface 211d of the second cylindrical portion 211 of the slinger 21. The thickness d1 of the elastic portion 13 on the first seal side is larger than the thickness d2 of the elastic portion 23 on the second seal side. Further, the fitting tightening allowance of the outer ring 2 on the inner peripheral surface 2b of the first seal side elastic portion 13 is set to be smaller than the fitting tightening allowance of the inner ring member 4 on the outer peripheral surface 4b of the second seal side elastic portion 23. Has been done. Further, a plurality of annular grooves 23a are formed on the inner peripheral surface of the second seal side elastic portion 23. The first seal side elastic portion 13 and the second seal side elastic portion 23 are formed to have a thickness larger than that of the second cylindrical portion 211. The length of the elastic portion 23 on the second seal side in the axial L direction is formed to be longer than the length of the elastic portion 13 on the first seal side in the axial L direction.

In the bearing seal 9 configured as described above, when the first seal member 10 and the second seal member 20 are combined, the third disk portion 213 and the second cylindrical portion 211 of the slinger 21 are formed. It is located in a straight line. In this state, the first sealing member 10 is assembled to the slinger 21 so that the axial lips 12a and the radial lips 12b and 12c are in contact with the predetermined surfaces of the second disk portion 212 and the second cylindrical portion 211, respectively. .. Further, the second disk portion 212 extends radially outward to a position where it overlaps with the reaction force generating portion 14 in the axial L direction. After that, the third disk portion 213 is bent so as to face outward in the radial direction at the other end portion 211b of the second cylindrical portion 211 which is thinned. Further, the garter spring 12d is elastically fitted to the outer peripheral portion of the radial lip 12c.

The bearing seal 9 in a state where the first seal member 10 and the second seal member 20 are combined in this way is press-fitted between the outer ring 2 and the inner ring member 4 by using a special jig (not shown). At the time of this press-fitting, a special jig is applied to the second side surface 212b of the second disk portion 212 in the slinger 21 and pressed toward the wheel side (bearing space S side) along the arrow a direction (press-fitting direction). The bearing seal 9 is press-fitted. In the initial stage of press-fitting, a pressing force by a dedicated jig is applied to the slinger 21, and the second cylindrical portion 211 of the slinger 21 starts fitting with the outer peripheral surface 4b of the inner ring member 4. At this time, the elastic portion 23 on the second seal side receives resistance due to the fitting tightening allowance with respect to the outer peripheral surface 4b of the inner ring member 4, so that the second cylindrical portion 211 of the slinger 21 is elastically strained by the elastic portion 23 on the second seal side. Is fitted with. Then, in the process of this fitting, the first side surface 212a of the slinger 21 abuts on the tip surface 14a of the reaction force generating portion 14, and the front end portion of the axial lip 12a is elastically deformed so as to be pressed and curved. do. In this state, when the second disk portion 212 of the slinger 21 is further pressed by the dedicated jig, the first side surface 212a of the second disk portion 212 is cored so as to be accompanied by elastic compression of the reaction force generating portion 14. Close to gold 11. At the same time, the pressing force is applied from the second disk portion 212 of the slinger 21 to the core metal 11 of the first seal member 10 via the reaction force generating portion 14. When a pressing force is applied to the core metal 11, the first cylindrical portion 111 of the core metal 11 starts fitting to the inner peripheral surface 2b of the outer ring 2. While the bearing seal 9 is press-fitted, the elastic portion 13 on the first seal side receives resistance due to the fitting tightening allowance with respect to the inner peripheral surface 2b of the outer ring 2, so that the first cylindrical portion 111 of the core metal 11 is the first seal. It is fitted with the elastic strain of the side elastic portion 13. When the second disk portion 212 is continuously pressed as it is, the fitting of the first cylindrical portion 111 to the outer ring 2 via the first seal side elastic portion 13 and the second seal side elastic portion 23 of the second cylindrical portion 211 are performed. Fitting to the inner ring member 4 via the inner ring member 4 proceeds in parallel. Then, when the first cylindrical portion 111 substantially reaches a predetermined fitting position, the pressing is released, whereby the press-fitting of the bearing seal 9 between the outer ring 2 and the inner ring member 4 is completed.

When the press-fitting is completed, the second seal member 20 is in the position shown by the two-dot chain line, and the first side surface 212a of the second disk portion 212 compresses the tip surface 14a of the reaction force generating portion 14 toward the wheel. It will be in an elastic contact state. Further, the elastic portion 13 on the first seal side and the elastic portion 23 on the second seal side are in a state where elastic strain is generated on the wheel side. When the jig is retracted and the pressure is released, the springback of the elastic portion 13 on the first seal side and the elastic portion 23 on the second seal side due to the elastic strain is generated via the first cylindrical portion 111 and the second cylindrical portion 211. It acts on the first seal member 10 and the second seal member 20, respectively. Therefore, the first seal member 10 and the second seal member 20 tend to move in the counter-press-fitting direction (direction opposite to the arrow a) along the axis L direction. At this time, the thickness d1 of the elastic portion 13 on the first seal side is larger than the thickness d2 of the elastic portion 23 on the second seal side, and the fitting tightening allowance for the outer ring 2 of the elastic portion 13 on the first seal side is the elastic portion on the second seal side. It is smaller than the fitting tightening allowance for the inner ring member 4. As a result, the amount of movement of the second seal member 20 along the axis L direction becomes larger than the amount of movement of the first seal member 10 along the axis L direction . As a result, a difference in the relative movement amount between the first seal member 10 and the second seal member 20 occurs, and the difference in the movement amount, the second seal member 20, separates from the first seal member 10 toward the vehicle body. Further, when the press-fitting is completed, the reaction force due to the compression of the reaction force generating portion 14 acts on the second seal member 20, and the movement of the second seal member 20 to the vehicle body side is promoted.

In the present embodiment, a reaction force due to elastic deformation of the axial lip 12a in a curved state is also generated. The reaction force generating portion 14 is formed so that the length in the axial L direction is shorter than that of the axial lip 12a and is thicker than the thickness (lip thickness) of the axial lip 12a. Therefore, the reaction force generating portion 14 has a higher rigidity than the axial lip 12a. The reaction force from the reaction force generating portion 14 acting on the second disk portion 212 is larger than the reaction force from the axial lip 12a. Therefore, the second seal member 20 can move more accurately in the direction away from the first seal member 10 due to the reaction force generated by the reaction force generating unit 14.

As described above, when the second seal member 20 is separated from the first seal member 10, the labyrinth r is between the tip surface 14a of the reaction force generating portion 14 and the first side surface 212a of the second disk portion 212. Occurs. The second seal member 20 shown by the solid line in FIG. 2 shows a state in which the seal member 20 is separated from the first seal member 10 and is stationary at a predetermined position. This labyrinth r corresponds to the amount of separation of the second seal member 20 from the first seal member 10, but this amount of separation does not cause springback to act on the first seal member 10 as in other embodiments described later. Smaller than the case. Therefore, the labyrinth r between the reaction force generating portion 14 and the second disk portion 212 can be accurately set to a minute state. As a result, the sealing performance of the labyrinth r is more accurately exhibited. Then, when the inner ring 5 rotates about the axis, the axial lip 12a elastically slides against the first side surface 212a of the second disk portion 211 of the slinger 21, and the radial lips 12b and 12c of the second cylindrical portion 211 of the slinger 21. It is elastically in relative sliding contact with the outer peripheral surface 211c. The elastic relative sliding contact of each of the seal lips 12a, 12b, 12c with respect to the slinger 21 and the presence of the labyrinth r prevent muddy water and the like from entering the bearing space S from the outside. Further, the lubricant filled in the bearing space S can be prevented from leaking to the outside.

In the present embodiment, the outer peripheral portion of the radial lip 12c is fitted with a garter spring 12d that elastically urges the radial lip 12c inward in the radial direction toward the center thereof, so that the sealing performance in this portion is enhanced. Be done. Further, by securing the labyrinth r, it is possible to reduce the rotational torque of the inner ring 5 with respect to the outer ring 2 and improve the sealing performance of the bearing seal 9. Further, since the second cylindrical portion 211 of the slinger 21 is provided with a third disk portion 213 extending radially outward from the other end portion 211b, this functions as a weir plate and further improves the sealing performance. Is planned. Further, by moving the second seal member 20 in the direction away from the first seal member 10, the elastic strain generated in the elastic portion 23 on the second seal side is corrected, and the plastic flow of the elastic portion 20 on the second seal side is reduced. Can be reduced.

FIG. 3 shows another embodiment of the sealing device according to the present invention. In the bearing seal (sealing device) 9 of the present embodiment, the first disk portion 112 extends radially inward from one end portion 111b of the first cylindrical portion 111 in the core metal 11 constituting the first seal member 10. It is formed. Then, the first cylindrical portion 111 is metal-fitted to the inner peripheral surface 2b of the outer ring 2 with a predetermined tightening margin without passing through the first seal-side elastic portion 13 as in the above embodiment. Similar to the above example, the first seal side seal body 12 is made of an elastomer such as a rubber material, wraps around one end 111a from a part of the outer peripheral surface 111c of the first cylindrical portion 111, and is inside the first cylindrical portion 111. Covers the peripheral surface 111d. Further, the first seal side seal body 12 is fixed and integrated with the core metal 11 so as to wrap around the inner diameter side end portion 112b from the first side surface 112a of the first disk portion 112 and reach the wheel side surface 112c. The first seal side seal body 12 is provided with an axial lip 12e extending toward the wheel side and a radial lip 12f that comes into contact with the outer peripheral surface 4b of the inner ring member 4. Further, in the first seal side seal body 12, the portion that goes around one end portion 111a of the first cylindrical portion 111 is referred to as a reaction force generating portion 14.

The second seal member 20 in the present embodiment includes a slinger 21 and a second seal side seal body 22. The slinger 21 has a second cylindrical portion 211 fitted to the outer peripheral surface 4b of the inner ring member 4 (inner ring 5) via a second seal-side elastic portion 23, and a radial outer side from one end portion 211a of the second cylindrical portion 211. Includes a second disc portion 212 that extends to and faces the first disc portion 112 in the L direction of the axis. The second seal side seal body 22 is made of an elastomer such as rubber as in the above example. The second seal side seal body 22 is integrally fixed from a part of the second side surface 212b of the second disk portion 212 so as to cover the entire inner peripheral surface 211d and the outer peripheral surface 211c of the second cylindrical portion 211. There is. Further, the second seal side seal body 22 is integrally fixed to the slinger 21 so as to cover the portion of the second disk portion 212 up to the majority of the wheel side surface 212a. The portion of the second seal-side seal body 22 that covers the other end portion 211b of the second cylindrical portion 211 is formed so as to be close to the facing first seal-side seal body 12 with a gap r1. The second seal-side elastic portion 23 is configured as a part of the second seal-side seal body 22 by a portion that covers the inner peripheral surface 211d of the second cylindrical portion 211. The second seal side seal body 22 is formed with two second seal side seal lips 22a and 22b extending toward the first disk portion 112 of the first seal member 10. The two second seal side seal lips 22a and 22b are positioned so as to sandwich the first seal side seal lip 12 in the radial direction. The second seal-side seal lip 22a on the outer side in the radial direction is formed so as to be close to the first seal-side seal body 12 with which the tip end portion 22aa faces, with a gap r1.

The bearing seal 9 of the present embodiment is also press-fitted between the outer ring 2 and the inner ring member 4 (inner ring 5) in a state where the first seal member 10 and the second seal member 20 are combined as shown in the drawing. Similar to the above example, the bearing seal 9 is press-fitted by pressing the second side surface 212b of the second disk portion 212 toward the bearing space S side with a dedicated jig. In the initial stage of press-fitting, a pressing force by a special jig is applied to the slinger 21, and the second cylindrical portion 211 of the slinger 21 is fitted to the outer peripheral surface 4b of the inner ring member 4 via the elastic portion 23 on the second seal side. To start. At this time, the elastic portion 23 on the second seal side is fitted with the elastic strain of the elastic portion 23 on the second seal side. Further, when pressed by the dedicated jig, the first side surface 212a of the second disk portion 212 abuts on the vehicle body side surface 14a of the reaction force generating portion 14 so as to be accompanied by elastic compression of the reaction force generating portion 14. At this time, the portion of the second seal side seal body 22 that covers the other end portion 211b of the second cylindrical portion 211 and the tip portion 22aa of the second seal side seal lip 22a are on the opposite portions of the first seal side seal body 12. Contact. Further, the pressing force is applied from the second disk portion 212 of the slinger 21 to the core metal 11 of the first seal member 10 via the reaction force generating portion 14. When a pressing force is applied to the core metal 11, the first cylindrical portion 111 of the core metal 11 starts to be fitted to the inner peripheral surface 2b of the outer ring 2. Since the fitting of the first cylindrical portion 111 to the outer ring 2 is a metal fitting, the fitting resistance is large, and the second cylindrical portion 211 is attached to the inner ring member 4 with a large elastic strain of the elastic portion 23 on the second seal side. It is fitted against it. Then, when the first cylindrical portion 111 substantially reaches a predetermined fitting position, the pressing is released, whereby the press-fitting of the bearing seal 9 between the outer ring 2 and the inner ring member 4 is completed.

When the press-fitting is completed, the first side surface 212a of the second disk portion 212 is in elastic contact so as to compress the reaction force generating portion 14 toward the wheel side. Further, the portion of the second seal side seal body 22 that covers the other end portion 211b of the second cylindrical portion 211 and the tip portion 22aa of the second seal side seal lip 22a are in contact with the first seal side seal body 12. .. Further, the elastic portion 23 on the second seal side is in a state where elastic strain is generated on the wheel side. When the jig is retracted and the press-fitting is released, the springback due to the elastic strain of the elastic portion 23 on the second seal side acts on the second cylindrical portion 211. Therefore, the second seal member 20 moves in the counter-press-fitting direction along the axis L direction. As a result, the second seal member 20 separates from the first seal member 10 toward the vehicle body. Further, after the press-fitting is completed, the reaction force due to the compression of the reaction force generating portion 14 acts on the second seal member 20, and the movement of the second seal member 20 toward the vehicle body side is promoted. Since the first seal member 10 is attached by metal fitting between the core metal 11 and the outer ring 2, the springback as described above does not act on the first seal member 10.

As described above, when the second seal member 20 is separated from the first seal member 10, the labyrinth r is formed between the vehicle body side surface 14a of the reaction force generating portion 14 and the wheel side surface 212a of the second disk portion 212. Occurs. Further, the tip portion 22aa of the second seal side seal lip 22a separates from the first seal side seal body 12, and the desired gap r1 is secured in this portion. Further, the portion of the second cylindrical portion 211 that covers the other end portion 211b is separated from the first seal side seal body 12 to secure a gap r2. Further, the second seal side seal body 22 and the axial lip 12e are separated from each other, and a gap r3 is secured. These gaps r1, r2, and r3 are configured as labyrinths. Then, when the inner ring 5 rotates about the axis, the radial lip 12f elastically comes into relative sliding contact with the outer peripheral surface 4b of the inner ring member 4. The elastic relative sliding contact of the radial lip 12f with respect to the inner ring member 4 and the presence of the labyrinths r, r1, r2, and r3 prevent muddy water and the like from entering the bearing space S from the outside. Further, the presence of the labyrinths r, r1, r2, and r3 and the alternating intrusion routes depending on the arrangement positions of the second seal side seal lip 22a, the first seal side seal lip 12e, and the second seal side seal lip 22b are combined. Therefore, the infiltration of muddy water or the like from the outside into the bearing space S is effectively suppressed. Moreover, since the first seal member 10 and the second seal member 20 are maintained in a non-contact state with each other, the rotational torque associated with the axial rotation of the inner ring member 4 is reduced while ensuring the sealing performance as the bearing seal 9. be able to.
Since the other configurations are the same as those of the above-described embodiment, the same reference numerals are given to the common portions, and the description thereof will be omitted.

In each embodiment, the thickness of the elastic portion 23 on the second seal side is made larger than the thickness of the second cylindrical portion 211, but the thickness is not limited to this. If the springback can be applied from the elastic portion 23 on the second seal side to the elastic portion 211 on the second seal side when the sealing device is press-fitted, for example, the thickness of the elastic portion 23 on the second seal side is the thickness of the second cylindrical portion. It may be formed so as to be smaller than the thickness of 211. Further, the shape of the reaction force generating portion 14 may be appropriately changed, and if the reaction force can be applied to the first sealing member or the second sealing member when the sealing device is press-fitted, the reaction force generating portion The shape of 14 may be changed as appropriate. Further, in the first embodiment, the thickness of the elastic portion 13 on the first seal side is formed to be larger than the thickness of the elastic portion 23 on the second seal side, but it may be changed so as to have the opposite relationship. .. Further, the second disk portion 212 of the slinger 21 of each embodiment may be provided with a magnetic material (magnetic rubber) for detecting the rotation speed. In this case, the magnetic material is pressed when the sealing device is press-fitted.

Further, although an example in which the sealing device according to the present invention is applied to the bearing seal of the bearing device 1 shown in FIG. 1, the example is described, but it can also be applied to the bearing seal 90. Further, in the embodiment, the outer ring 2 is used as one member and the inner ring 5 is used as the other member, but these may have the opposite relationship. Further, although the example in which the reaction force generating portion 14 is provided on the first seal member 10 is shown, it may be provided on the second seal member 20. In addition, in each embodiment, an example in which the sealing device according to the present invention is applied to a bearing device for an automobile has been described, but the present invention is not limited to this, and the space between the inner member and the outer member that rotate relative to each other is not limited to this. As long as it is a sealing device mounted by press fitting, it is preferably applied to a sealing device in other industrial fields. For example, the sealing device according to the present invention may be applied to an oil seal which is arranged between a housing and a rotating shaft to prevent oil leakage in the housing. Further, the bearing device for an automobile may be a bearing device of another form, not limited to the bearing device shown in FIG. 1, and may be a bearing device for a driven wheel, not limited to a drive wheel. .. Further, the shapes and numbers of the constituent members (core metal, seal lip, slinger, etc.) of the first seal member 10 and the second seal member 20 can be appropriately changed according to the required specifications and the like.

2 Outer ring (outer member, one member)
3 Hub wheel (inner member)
4 Inner ring member (inner member)
5 Inner ring (inner member, other member)
9 Bearing seal (sealing device)
10 1st seal member 11 Core metal 111 1st cylindrical part 111a One end 111b Other end 112 1st disk part 12 1st seal side seal body 12a Axial lip (1st seal side seal lip)
13 1st seal side elastic part 14 Reaction force generating part 20 2nd seal member 21 Slinger (2nd seal member)
211 Second cylindrical part 211a One end part 212 Second disk part
23 2nd seal side elastic part
a Press-fitting direction d1 Thickness of the elastic part on the first seal side d2 Thickness of the elastic part on the second seal side L-axis

Claims (4)

The inner side is in a state where the first seal member attached to one of the inner and outer members that rotate relative to the axis and the second seal member attached to the other member of the inner member and the outer member are combined. A sealing device that is mounted in a state of being press -fitted between a member and the outer member and used to seal between the inner member and the outer member.
The first seal member includes a core metal having a first cylindrical portion fitted to the one member and a first disk portion extending radially from one end of the first cylindrical portion, and the core metal. Including the attached first seal side seal body,
The second seal member extends radially from one end of the second cylindrical portion and the second cylindrical portion fitted to the other member via the second seal side elastic portion made of an elastic material, and also has a shaft. Including the second disk portion facing the first disk portion in the direction, and in the press-fitted state, the entire second seal member is shafted by the elastic strain of the second seal side elastic portion. It is allowed to move in the direction,
In the state of being press -fitted into one of the first seal member and the second seal member, the first seal member and the other of the second seal member are elastically contacted in a direction opposite to the press-fit direction. A reaction force generating part that generates a reaction force is provided ,
A sealing device characterized in that the second seal member is separated from the first seal member in a direction opposite to the press-fitting direction by the action of the reaction force generating portion and the elastic portion on the second seal side . In the sealing device according to claim 1,
The first seal side seal body includes a first seal side seal lip that comes into contact with the second disk portion.
The reaction force generating portion is provided on the first seal side seal body and is formed so as to have a shorter axial length and a thicker thickness than the first seal side seal lip. 2 A sealing device characterized in that it is configured to come into contact with a disk portion. In the sealing device according to claim 1 or 2.
The first cylindrical portion of the first seal member is fitted to the one member via the elastic portion on the first seal side made of an elastic material.
The thickness of the elastic portion on the first seal side is larger than the thickness of the elastic portion on the second seal side, and the fitting tightening allowance for the one member of the elastic portion on the first seal side is the other elastic portion on the second seal side. A sealing device characterized by being smaller than the fitting tightening allowance for a member of. In the sealing device according to any one of claims 1 to 3.
The second seal member is a sealing device having a second seal side seal body provided with a second seal side seal lip close to the first seal member.

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