JP6253188B2 - Bearing sealing device - Google Patents

Description

  The present invention relates to a bearing sealing device used for a bearing device of a wheel support portion of, for example, an automobile, and more particularly to a bearing sealing device having a function of discharging muddy water that has entered the bearing sealing device to the outside of the bearing device. .

  The above-described bearing sealing device of the automobile bearing device is mounted on the axial end portion of the annular bearing space between the rotating side member and the fixed side member that supports the rotating side member so as to be coaxially rotatable. As such a bearing sealing device, a first member that is integrally attached to a rotation side member (for example, an inner ring) and an elastic body that is integrally attached to a fixed side member (for example, an outer ring) and elastically contacts the first member. A pack seal type bearing sealing device including a second member having a seal lip is often used. The bearing sealing device of such a bearing device is exposed to a harsh environment due to an attack such as muddy water, and the muddy water or the like into the bearing space even when the rotating side member is rotating (while the wheel is rotating). It is required to prevent intrusion. For this reason, it is necessary to bring the plurality of seal lips into sliding contact with the first member so that the sealing function by sliding contact with the first member of the sealing lip is reliably exhibited and maintained. In addition, if muddy water or the like enters the bearing sealing device, the seal lip tip wears due to the muddy water or the like entering the sliding contact portion and the sealing function deteriorates, so the outside air side (the side opposite to the bearing space) ) Part of the first member is also provided with a seal lip to be brought into sliding contact with the second member. However, as the sliding contact portion increases, the rotational torque of the rotating side member increases, and in particular, in a bearing sealing device for an automotive bearing device, it is difficult to achieve both maintenance of the sealing function and reduction in torque. A drastic improvement was desired.

Therefore, in Patent Documents 1 to 5, a small gap or a labyrinth structure is formed between the facing portions of the first member and the second member on the outside air side, and further, muddy water or the like enters the bearing sealing device from the small gap. There has been proposed a bearing sealing device that takes measures against muddy water to discharge the muddy water or the like that has entered. Hereinafter, the technical contents described in each patent document will be outlined.
Patent Document 1 discloses a bearing sealing device in which a plurality of foreign matter (muddy water) elimination fins are provided in the circumferential direction on the inner surface of the inner ring side annular portion of the inner ring side metal ring (first member) to take the muddy water countermeasure. Is described.
In the wheel bearing device described in Patent Document 2, the magnetic rubber attached to the outer surface side of the annular portion of the slinger (first member) is made to wrap around from the tip portion of the annular portion to the inner surface side. The muddy water countermeasure is taken in a gap between the portion and the rubber member of the seal member (second member). Specifically, by inclining this gap outward in the axial direction and radially outward, the gap is lengthened, making it difficult for muddy water to enter the bearing sealing device from the gap and entering the bearing sealing device. The muddy water is discharged by the centrifugal force accompanying the rotation of the wheel.
In Patent Document 3, an outer diameter surface of a wraparound portion of a magnetic encoder that covers an outer diameter portion of a slinger (first member) and an inner diameter surface of an opening end portion of a seal member (second member) are opposed to each other. There is described a wheel bearing device in which an inner diameter surface of a portion is formed on a tapered surface inclined toward an outer diameter side. In addition, the outer diameter surface of the wraparound portion and the inner diameter surface of the opening end portion form a labyrinth seal, and the tapered surface and the labyrinth seal serve to prevent muddy water from entering the bearing sealing device (muddy water resistance performance). ) Is improved, and intruded muddy water is discharged by centrifugal force.
Patent Document 4 is a bearing sealing device in which a second seal member (first member) is provided with a seal lip, and this seal lip is configured to elastically contact the first seal member (second member), A bearing sealing device in which a pumping action portion is provided on the second seal member is described. This pumping action part has a function of discharging muddy water or the like that has entered the bearing sealing device out of the bearing sealing device.
In Patent Document 5, a labyrinth seal is configured by an outer edge of a slinger (first member) and a seal plate (second member) facing each other with a slight radial gap, and is adhered to a side surface of the slinger. A bearing sealing device in which cut grooves are formed at corners of an outer diameter portion of a magnetic encoder is described. The cut groove is inclined to the outer diameter side, and prevents labyrinth and the like from entering the bearing sealing device by the labyrinth seal and promotes the discharge of mud and the like.

JP-A-2005-98417 JP 2007-285499 A JP2011-99464A Japanese Patent No. 4501472 JP 2013-44420 A

By the way, the muddy water countermeasure disclosed in Patent Document 1 is a method in which muddy water or the like to enter the bearing sealing device through a gap between the outer metal ring (second member) and the inner metal ring is removed by a foreign matter eliminating fin. Is going to be discharged from the outside. However, it is understood that there is no idea that the gap itself has a function of actively preventing the intrusion of muddy water or the like into the bearing sealing device. In this case, muddy water or the like entering along the inner metal ring is excluded by the foreign matter removing fins, but muddy water or the like entering along the outer metal ring is considered to be difficult to be excluded.
The muddy water countermeasure disclosed in Patent Document 2 makes it difficult for muddy water to enter the bearing sealing device and from the clearance between the rubber rubber part of the sealing member and the rubber member of the sealing member. The muddy water is discharged by the centrifugal force accompanying the rotation of the wheel. Such a function is supposed to be achieved by the above-described formation mode of the gap. However, since both opposing surfaces of the gap are smooth, muddy water or the like that has entered the bearing sealing device is actively discharged. It is thought that the function is not fully exhibited.
The countermeasure against muddy water disclosed in Patent Document 3 is to improve the function of preventing muddy water from entering the bearing sealing device by the tapered surface and the labyrinth seal, and to discharge muddy water that has entered by centrifugal force. is there. However, in this case as well, it is considered that both opposing surfaces forming the labyrinth seal are smooth and the function of actively discharging muddy water or the like that has entered the bearing sealing device is not fully exhibited.

Further, the muddy water countermeasure disclosed in Patent Document 4 has a function of discharging muddy water or the like entering the bearing sealing device to the outside of the bearing sealing device by the pumping action portion provided in the second seal member. However, this pumping action part does not exist in the gap portion where the first member and the second member face each other on the outside air side (the side opposite to the bearing space). For this reason, it is considered that the function of preventing the intrusion of muddy water or the like is not sufficiently exhibited.
The countermeasure against muddy water disclosed in Patent Document 5 prevents muddy water from entering the bearing sealing device by the cut grooves formed in the corners of the outer diameter portion of the magnetic encoder and the labyrinth seal, and muddy water or the like. It has a function to promote discharge. However, since the cut groove is formed at the corner of the outer diameter portion of the magnetic encoder, it is considered that the function of discharging muddy water or the like that has entered the bearing sealing device to the outside is not sufficiently exhibited. Moreover, in this patent document 5, the opposing surface by the side of the sealing board which comprises a labyrinth seal is made into the taper surface which expands toward an opening part. Therefore, an opening part becomes large and muddy water by a notch groove | channel. Even if there is an effect such as shaking off, it is considered that the function of suppressing the intrusion of muddy water is insufficient. In particular, the cut grooves are formed in the corners of the outer diameter portion of the magnetic encoder, so that muddy water entering along the magnetic encoder (inner member) is excluded, but enters along the outer member. It is thought that mud water that comes is hard to be excluded.

  The present invention has been made in view of the above circumstances, and provides a bearing sealing device capable of accurately preventing the intrusion of muddy water into the bearing sealing device and discharging the intruded muddy water while reducing the rotational torque. The purpose is to do.

A bearing sealing device according to the present invention is a bearing sealing device mounted on an axial end portion of an annular bearing space in a bearing device in which a rotating side member is supported so as to be coaxially rotatable with respect to a fixed side member. A first member constituting a part of the rotating side member with a metal ring integrally attached to the side member; a core metal integrally attached to the fixed side member; and a metal core fixed to the metal core and fixed to the metal ring A second member constituting a part of the fixed side member having a seal lip member having an elastic seal lip that is elastically contacted, wherein the rotating side member and the fixed side member are opposite to the bearing space. The labyrinth structure is formed in the portion, and the opposing surfaces forming the labyrinth structure in the rotating side member and the stationary side member are parallel to each other, and are tapered surfaces that expand in diameter toward the opposite side to the bearing space. Have Has an elastic member is secured to the radial end portion of the metal ring through the anchoring base, said resilient member, said the anchoring base from the bearing space is formed so as to protrude to the opposite side, the elastic members and The fixed side member has the tapered surfaces that form the labyrinth structure, and either one of the tapered surfaces is provided with muddy water discharge means.

According to the present invention, the rotating side member and the stationary side member form a labyrinth structure on the opposite side (outside air side) from the bearing space, so that intrusion of muddy water or the like from the outside air into the bearing sealing device is suppressed. Is done. In addition, since the opposing surfaces of the rotating side member and the stationary side member forming the labyrinth structure are parallel to each other and have tapered surfaces that increase in diameter toward the outside air side, bearing sealing from the outside air side is possible. Intrusion of muddy water or the like into the apparatus is more effectively suppressed. The muddy water discharging means further promotes the function of suppressing the intrusion of the muddy water into the bearing sealing device, and the muddy water that has entered the bearing sealing device is also sequentially discharged out of the bearing sealing device to enter the bearing sealing device. The amount of accumulated muddy water can be reduced. Therefore, when the first member is rotated, muddy water or the like is less likely to be caught in the sliding contact portion of the seal lip with respect to the first member, and wear of the seal lip due to the biting of muddy water is less likely to occur. As a result, the life of the bearing sealing device can be extended. Further, the number of seal lips can be reduced, and the rotational torque can be reduced while maintaining the muddy water resistance. Moreover, since the opposing surfaces of the elastic member and the fixed side member forming the labyrinth structure are parallel to each other and have tapered surfaces that increase in diameter toward the outside air side, the inside of the bearing sealing device from the outside air side Intrusion of muddy water into the water is more effectively suppressed.

In the present invention, it may be as the mud discharge means is provided on the tapered surface of the front Symbol elastic member. According to this, the function of suppressing intrusion into the bearing sealing device of the muddy water is further promoted by the swing-off action accompanying the rotation of the muddy water discharging means provided on the tapered surface of the elastic member as a part of the rotation side member, The muddy water that has entered the bearing sealing device is also sequentially discharged out of the bearing sealing device, and muddy water and the like remaining in the bearing sealing device can be reduced.

In the present invention, the elastic member of the rotating member and the seal lip member may each have the tapered surface that forms the labyrinth structure. According to the present invention, the opposing surfaces of the elastic member of the rotating side member forming the labyrinth structure and the seal lip member have a tapered surface that is parallel to each other and expands toward the outside air. Intrusion of muddy water or the like into the bearing sealing device from the outside air side is more effectively suppressed. In this case, the muddy water discharging means may be provided on the tapered surface of the seal lip member. According to this, mud etc. are efficiently discharged | emitted along the muddy water discharge | release means provided in the seal lip member by rotation of the rotation side member.

In the present invention, the width of the taper surface of the fixed side member may be larger than the width of the taper surface of the rotation side member.
According to the present invention, by making the width of the taper surface of the fixed side member larger than the width of the taper surface of the rotation side member, the taper surface of the fixed side member acts to guide muddy water or the like to the centrifugal side. And this and the action by the muddy water discharging means combine, and the muddy water discharging function is more effectively exhibited. In addition, the muddy water that has entered the bearing sealing device is sequentially discharged to the outside air along the tapered surface of the stationary member.

In the present invention, the muddy water discharging means may be configured by a convex portion and a concave portion that are repeatedly formed on one of the tapered surfaces along the circumferential direction.
According to the present invention, due to the synergistic action between the airflow generated with the rotation of the first member and the convex and concave portions that are repeatedly formed along the circumferential direction, the suppression and discharge of muddy water and the like is more effectively performed. Made. In particular, when the first member is provided with muddy water discharge means, the projection and the recess also rotate with the rotation of the first member. Intrusion control and discharge are more effective. Further, the convex portion or the concave portion has a function of guiding mud water or the like to the outside air side (opposite side to the bearing space), and mud water or the like is efficiently discharged along the convex portion or the concave portion by the centrifugal force due to rotation.
In this case, the concave portion of the muddy water discharging means may be composed of a plurality of groove-shaped portions, and the convex portion may be composed of a portion between the groove-shaped portions. According to this, the intrusion of muddy water and the like is suppressed and discharged by the synergistic action of the airflow generated with the rotation of the first member and the groove-shaped portion formed repeatedly along the circumferential direction and the portion between the groove-shaped portions. Is made more effective. In particular, when the muddy water discharging means is provided in the first member, the portion between the groove shape portion and the groove shape portion also rotates with the rotation of the first member. Due to the airflow generated by the rotation, the intrusion of muddy water or the like into the bearing sealing device is more effectively suppressed and discharged. The groove-shaped portion has a function of guiding muddy water or the like to the outside air side (opposite to the bearing space), and muddy water or the like is efficiently discharged along the groove-shaped portion by the centrifugal force due to rotation.

Further, the convex portion of the muddy water discharge means may be composed of a plurality of blade-shaped portions, and the concave portion may be composed of a portion between the blade-shaped portions. According to this, the intrusion of muddy water and the like is suppressed and discharged by the synergistic action between the airflow generated with the rotation of the first member and the blade shape portion formed repeatedly along the circumferential direction and the portion between the blade shape portions. Is made more effective. In particular, when the first member is provided with muddy water discharging means, the portion between the blade shape portion and the blade shape portion also rotates with the rotation of the first member. The air flow generated by the rotation more effectively suppresses and discharges muddy water and the like into the bearing sealing device. Further, the blade-shaped portion has a function of guiding muddy water or the like to the outside air side (opposite to the bearing space), and muddy water or the like is efficiently discharged along the blade-shaped portion by centrifugal force due to rotation.
Furthermore, the convex part of the muddy water discharge means may be composed of a plurality of mountain-shaped parts, and the concave part may be a valley-shaped part between the mountain-shaped parts. According to this, due to the synergistic action between the airflow generated with the rotation of the first member and the mountain-shaped portion repeatedly formed along the circumferential direction and the valley-shaped portion between the mountain-shaped portions, muddy water, etc. Invasion is suppressed and discharged more effectively. In particular, when the first member is provided with a muddy water discharging means, the mountain-shaped portion and the valley-shaped portion between the mountain-shaped portions rotate as the first member rotates. Due to the airflow generated with the rotation of the valley-shaped portion between the mold-shaped portions, the intrusion of muddy water or the like into the bearing sealing device is more effectively suppressed and discharged.

In the present invention, a minimum gap between the muddy water discharging means and the other tapered surface facing the muddy water discharging means may be set to 0.1 to 1.00 mm.
According to the present invention, by setting the minimum gap to 0.1 to 1.00 mm, infiltration of muddy water or the like and discharge of muddy water or the like that has entered is suitably achieved. Incidentally, when the minimum gap is less than 0.1 mm, the opposing surfaces may come into contact with each other due to design tolerances or the like. On the other hand, if the thickness exceeds 1.00 mm, the function of preventing infiltration of muddy water or the like into the bearing sealing device tends to be insufficiently exhibited.

  According to the present invention, it is possible to provide a bearing sealing device that can accurately prevent the intrusion of muddy water into the bearing sealing device and discharge the intruded muddy water while reducing the rotational torque.

It is a schematic longitudinal cross-sectional view which shows an example of the bearing apparatus with which the bearing sealing apparatus which concerns on this invention is applied. It is an enlarged view of the A section of Drawing 1, and is a figure showing one embodiment of the bearing sealing device concerning the present invention. It is the same figure as FIG. 2 which shows the modification of the embodiment. (A) is a figure which shows typically the state which expand | deployed the BB arrow line part in FIG. 2, (b) (c) (d) is the same figure of another form. (A) is CC sectional view taken on the line in FIG. 4 (a), (b) is the same which shows the modification. FIG. 4C is a cross-sectional view taken along line DD in FIG. It is a figure similar to FIG. 2 which shows another embodiment of the bearing sealing device which concerns on this invention. It is the same figure as FIG. 2 which shows the modification of the embodiment. It is a figure similar to FIG. 2 which shows another modification of the embodiment. It is the same figure as FIG. 2 which shows another modification of the embodiment. It is the same figure as FIG. 2 which shows another embodiment of the bearing sealing device which concerns on this invention. It is the same figure as FIG. 2 which shows the modification of the embodiment. It is a figure similar to FIG. 2 which shows another modification of the embodiment. It is the same figure as FIG. 2 which shows another modification of the embodiment. It is a figure similar to FIG. 2 which shows other embodiment of the bearing sealing device which concerns on this invention. It is a figure similar to FIG. 2 which shows other embodiment of the bearing sealing device 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 supports a drive wheel (not shown) of an automobile so as to be rotatable. The bearing device 1 generally includes an outer ring (fixed side member) 2, a hub ring 3, an inner ring member 4 fitted and integrated with the vehicle body side of the hub ring 3, an outer ring 2, a hub ring 3, and an inner ring. A hub bearing including two rows of rolling elements (balls) 8 interposed between the members 4. In this example, the hub ring 3 and the inner ring member 4 constitute an inner ring (rotation side member) 5. The outer ring 2 is fixed to a vehicle body (not shown) of the automobile. The hub wheel 3 is coaxially spline-fitted to a drive shaft 7 connected to a drive source (not shown) via a constant velocity joint 6 and is connected to the drive shaft 7 by a nut 7a so as not to be detached. Has been. The inner ring 5 (the hub ring 3 and the inner ring member 4) can be coaxially rotated 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. In the bearing space S, two rows of rolling elements 8... Roll the raceway 2 a of the outer ring 2, the raceway 3 a of the hub ring 3, and the raceway 4 a of the inner ring member 4 while being held by the retainer 8 a. It is possible to intervene. The hub wheel 3 has a cylindrical hub wheel body 30 and a hub flange 31 formed so as to extend radially outward from one wheel side end of the hub wheel body 30. The wheel is attached and fixed by the illustrated nut.
In the present specification, the side facing the wheel along the axis L direction (the side facing the left side in FIG. 1) 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 and 10 are attached to both ends of the bearing space S along the axis L direction, between the outer ring 2 and the hub ring 3 and between the outer ring 2 and the inner ring member 4. Both end portions along the direction of the axis L of the space S are sealed. This prevents intrusion of muddy water or the like into the bearing space S and leakage of the lubricant (grease or the like) filled in the bearing space S to the outside. These bearing seals 9 and 10 correspond to the bearing sealing device of the present invention. As an embodiment of the bearing sealing device according to the present invention, a bearing seal (bearing sealing device) 10 on the vehicle body side will be described with reference to FIG. I will explain.

  A bearing seal 10 shown in FIG. 2 includes a slinger (metal ring) 11 fitted to the outer diameter surface 4b of the inner ring member 4 (inner ring), a core metal 14 fitted to the inner diameter surface 2b of the outer ring 2, and a core. This is a pack seal type bearing seal composed of an elastic seal lip member 17 fixed to the gold 14. More specifically, the slinger 11 includes a cylindrical portion (hereinafter referred to as a slinger cylindrical portion) 12 fitted to the outer diameter surface 4b of the inner ring member 4, and one end portion of the slinger cylindrical portion 12 (the vehicle body side in the illustrated example). End portion) 12a and an outward flange 13 extending to the outer diameter side. The slinger 11 is formed of stainless steel (for example, SUS430), titanium steel, or SPCC steel plate subjected to surface treatment such as plating. The cored bar 14 includes a cylindrical part (hereinafter referred to as a cored bar cylindrical part) 15 fitted to the inner diameter surface 2b of the outer ring 2, and one end of the cored bar cylindrical part 15 (an end part on the wheel side in the illustrated example) 15a. It consists of an inward flange 16 that extends further to the inner diameter side. The seal lip member 17 is made of an elastomer material such as rubber or elastic resin, and is integrally fixed to a predetermined portion of the core metal 14 by molding. The seal lip member 17 of the present embodiment includes three seal lips 17a, 17b, and 17c that elastically contact the slinger 11. Further, the seal lip member 17 has a seal lip base 170 integrally fixed to a vehicle body side surface 16a of the inward flange portion 16 of the core metal 14 and an inner diameter surface 15b of the core metal cylindrical portion 15, and the seal lip 17a, 17 b and 17 c extend from the seal lip base 170 toward the slinger 11. The seal lip base 170 further wraps around the wrapping portion 170a that wraps around the inner diameter side end portion 16b of the inward flange portion 16 and reaches the wheel-side surface 16c, and the other end portion 15c on the vehicle body side of the core metal cylindrical portion 15. And a wraparound portion 170b that reaches the outer diameter surface 15d of the cored bar cylindrical portion 15 is provided. An annular protrusion 170c that is interposed in a compressed state at a fitting portion between the cored bar cylindrical portion 15 and the outer ring 2 is formed in the wraparound portion 170b. FIG. 2 shows a state in which the annular protrusion 170c is compressed, and a two-dot chain line shows its original shape. The seal lip 17 a is an axial lip that elastically contacts the wheel-side surface 13 a of the outward flange 13 of the slinger 11, and the seal lips 17 b and 17 c are radial lips that elastically contact the outer diameter surface 12 b of the slinger cylindrical portion 12 of the slinger 11. It is.

  An elastic member 18 is fixed to the outer diameter side end 13 b of the outward flange 13 in the slinger 11. The elastic member 18 has a fixed base 180 that covers the vehicle body side surface 13c of the outward flange 13 and wraps around the outer diameter side end 13b to reach the wheel side surface 13a of the outward flange 13. Is formed in a lip shape extending from the outer diameter side end portion of the fixing base portion 180 so as to be bent toward the vehicle body side after protruding toward the wheel side. When the slinger 11 is fitted to the inner ring member 4, the inner diameter side end 180 a of the fixing base 180 is formed so as to be interposed between the slinger 11 and the inner ring member 4 and block the fitting part of both. . The elastic member 18 including the fixing base portion 180 is made of an elastomer material such as rubber or elastic resin similar to that described above, and is formed integrally with the portion of the slinger 11 by molding. A portion including the slinger 11 and the elastic member 18 is integrally attached to the inner ring member 4 by fitting the slinger cylindrical portion 12 to the inner ring member 4, and the first member 100 constituting a part of the rotation side member; Is done. Further, a portion including the cored bar 14 and the seal lip 17a (17b, 17c) is integrally attached to the outer ring 2 by fitting the cored bar cylindrical portion 15 to the outer ring 2 to constitute a part of the fixed side member. It is set as the 2nd member 200 to do.

  The cored bar 14 and the seal lip member 17 that form part of the fixed side member, and the slinger 11 and the elastic member 18 that form part of the rotating side member form a labyrinth structure r1 on the opposite side of the bearing space S. To do. Specifically, the labyrinth structure r1 is formed by the portion of the seal lip member 17 that covers the inner diameter surface 15b of the core metal cylindrical portion 15 of the seal lip base portion 170 and the elastic member 18, and each labyrinth structure r1 is formed. The opposing surfaces 170d and 18a are parallel to each other, and are tapered surfaces that increase in diameter toward the side opposite to the bearing space S (the vehicle body side in the illustrated example). The widths d1 and d2 of the opposed surfaces 170d and 18a forming the tapered surfaces (the tapered surface widths) d1 and d2 are set such that the tapered surface width d1 of the former opposed surface 170d is larger than the tapered surface width d2 of the latter opposed surface 18a. (Refer to the enlarged portion in FIG. 2). The opposing surface (tapered surface) 18a of the elastic member 18 is provided with muddy water discharging means 19 composed of convex portions 19a and concave portions 19b repeatedly formed along the circumferential direction, as will be described later. . Here, the minimum gap d3 between the facing surface 170d as the fixed side member and the muddy water discharge means 19 (convex portion 19a) is set to 0.1 to 1.00 mm. Further, the taper angle of the opposing surfaces (tapered surfaces) 170d, 18a with respect to the axis L is set to 5 ° to 60 °, preferably 5 ° to 45 °.

  FIG. 3 shows a modification of the embodiment. In the bearing seal (bearing sealing device) 10A of this example, the shape of the elastic member 18 and the shapes of the cored bar 14 and the seal lip member 17 are different from the above example. That is, the elastic member 18 extends to the vehicle body side as it is from the outer diameter side end portion of the fixed base portion 180. Further, the cored bar 14 has an outward flange part 15e extending from the other end part 15c of the cored bar cylindrical part 15 in parallel to the vehicle body side end surface 2c of the outer ring 2 in the outer diameter direction. The seal lip base 170 of the seal lip member 17 covers the surface 15ea on the vehicle body side of the outward flange 15e, and also has an outer diameter that goes around the outer diameter side end 15eb of the outward flange 15e and reaches the wheel-side surface 15ec. A direction extending portion 170e is provided. Further, a branch extending portion 170f that branches from the extending base portion of the outer diameter extending portion 170e to the vehicle body side is formed. The branch extending portion 170f and the elastic member 18 form a labyrinth structure r2, and the opposing surfaces 170d and 18a forming the labyrinth structure r2 are parallel to each other and opposite to the bearing space S. The taper surface is increased in diameter. The opposing surface 170d here is formed so as to form a continuous surface from the portion covering the cored bar cylindrical portion 15 in the seal lip base portion 170 to the branch extending portion 170f, and the width d1 of the tapered surface is as described above. Similarly, it is made larger than the width d2 of the taper surface in the opposing surface 18a. And the muddy water discharge means 19 is provided in the opposing surface (taper surface) 18a of the elastic member 18. As shown in FIG. Also in this example, the part provided with the slinger 11 and the elastic member 18 is the first member 100, and this first member 100 constitutes a part of the rotation side member. Moreover, the part provided with the metal core 14 and the seal lips 17a (17b, 17c) is the second member 200, and the second member 200 constitutes a part of the fixed side member. Since the other configuration is the same as the example shown in FIG. 2, the same reference numerals are given to the common parts, and the description thereof is omitted.

Next, the muddy water discharging means 19 will be described with reference to FIGS. FIG. 4 is a diagram schematically showing a state where the BB line arrow portion in FIG. 2 is developed, and (a) to (d) show various aspects thereof. These are common to similar parts shown in FIG. In Fig.4 (a), the some convex part 19a (recessed part 19b) or the recessed part 19b (convex part 19a) which comprises the muddy water discharge | release means 19 is repeatedly formed in the circumferential direction (helical shape). It is formed to make. Moreover, in FIG.4 (b), the some convex part 19a (recessed part 19b) or the recessed part 19b (convex part 19a) is formed so that the V-shape repeatedly formed along the circumferential direction may be made. Furthermore, in FIG. 4C, the plurality of convex portions 19a (concave portions 19b) or concave portions 19b (convex portions 19a) form a part of a V-shape that is repeatedly formed along the circumferential direction (C). (Shape). Further, in FIG. 4D (see also FIG. 5C), the convex portion 19a is formed of a mountain-shaped portion, and the concave portion 19b is formed of a valley-shaped portion between the convex portions 19a formed of the mountain-shaped portion. It is formed as follows.
4A, 4B, and 4C, the projections 19a and the recesses 19b of the muddy water discharge means 19 have a groove shape as shown in FIG. 5A, or as shown in FIG. Since there may be a blade shape, for convenience, the portions indicated by the lead lines are given two types of symbols, a convex portion 19a and a concave portion 19b. Further, the mountain-shaped portion 19a and the valley-shaped portion 19b in the examples shown in FIGS. 4D and 5C are formed over the entire width direction of the opposing surface (tapered surface) 18a of the elastic member 18. Although not shown, the muddy water discharging means 19 indicated by the broken line in FIGS. 2 and 3 is provided in the outside air side portion of the tapered surface 18a in this example. The same applies to the following examples.

  5 (a) and 5 (b) show a cross-sectional view taken along the line CC in FIG. 4 (a), and correspond to the same cross-sectional view in FIGS. 4 (b) and 4 (c). FIG. 5A shows a plurality of concave portions 19 b constituting the muddy water discharging means 19, each having a groove-shaped portion and formed so as to dent the opposing surface (tapered surface) 18 a, and a plurality of convex portions constituting the muddy water discharging means 19. 19a shows that it consists of the part between these groove-shaped parts (concave part 19b). In FIG. 5B, the plurality of convex portions 19a constituting the muddy water discharging means 19 are composed of blade (fin) -shaped portions and are formed so as to protrude from the opposing surface (tapered surface) 18a. It is shown that the plurality of concave portions 19b are formed of portions between these blade-shaped portions (convex portions 19a). FIG. 5C is a cross-sectional view taken along the line D-D in FIG. 4D, and a plurality of mountain-shaped portions are formed on the vehicle body side half of the opposing surface (tapered surface) 18a. It is shown that the convex portions 19a are formed at substantially equal intervals along the circumferential direction, and the valley-shaped portion between the convex portions 19a is a concave portion 19b. The convex portion 19a and the concave portion 19b are simultaneously formed by molding when the elastic member 18 is formed integrally with the slinger 11. Alternatively, the muddy water discharge means 19 can be configured by scraping the confronting surface (tapered surface) 18a of the concave portion 19b with a laser or a blade.

  The bearing seals 10 and 10A shown in FIG. 2 or 3 having the muddy water discharging means 19 as shown in FIGS. 4 and 5 are provided between the outer ring 2 and the inner ring 5 (inner ring member 4) of the bearing device 1 shown in FIG. The end of the bearing space S on the vehicle body side is sealed. Specifically, the first member 100 is attached to the outer diameter surface 4 b of the inner ring member 4 by fitting, and the second member 200 is attached to the inner diameter surface 2 b of the outer ring 2 by fitting. In the fitted state of the first member 100 with respect to the inner ring member 4, the inner diameter side end portion 180 a of the fixed base portion 180 of the elastic member 18 covers the fitting portion between the slinger cylindrical portion 12 and the outer diameter surface 4 b of the inner ring member 4. Therefore, there is no concern that muddy water or the like enters the fitting portion between the metals. In the example shown in FIG. 2, when the second member 200 is fitted to the outer ring 2, the annular protrusion 170 c formed on the seal lip base 170 is between the core metal cylindrical part 15 and the inner diameter surface 2 b of the outer ring 2. Therefore, there is no fear that muddy water or the like enters the fitting portion between the metal of the core metal cylindrical portion 15 and the outer ring 2. Further, in the example shown in FIG. 3, since the radially extending portion 170 e reaches the wheel-side surface 15 ec of the outward flange 15 e, this portion is the outer ring 2 in the fitted state of the second member 200 with respect to the outer ring 2. It is interposed in a compressed state between the vehicle body side end surface 2c and the outward flange 15e. Accordingly, there is no concern that muddy water or the like enters the metal fitting portion of the core metal cylindrical portion 15 and the outer ring 2.

  When the bearing seals 10 and 10A are mounted as described above, the seal lips 17a, 17b, and 17c elastically contact the slinger 11, and the labyrinth structures r1 and r2 are formed on the vehicle body side portions of the first member 100 and the second member 200. It is formed. As the drive shaft 7 rotates about the axis L, the inner ring 5 and the first member 100 rotate integrally around the axis L. With this rotation, the seal lips 17a, 17b, and 17c are in sliding contact with the slinger 11 in a state of elastic contact. As a result, the end of the bearing space S on the vehicle body side is sealed to prevent entry of muddy water into the bearing space S or leakage of lubricant (grease, etc.) filled in the bearing space S to the outside. Is done. At this time, muddy water or the like tends to enter the space 300 surrounded by the first member 100 and the second member 200 from the gap between the opposing surfaces 170d and 18a. However, since the opposing surfaces 170d and 18a form the labyrinth structures r1 and r2, the infiltration of the muddy water or the like is suppressed by the labyrinth structures r1 and r2. In particular, since the minimum gap d3 in the labyrinth structures r1 and r2 is set to be smaller than 1.00 mm, the function of suppressing the intrusion of muddy water or the like is effectively exhibited. In addition, since the opposing surface 18a of the elastic member 18 is provided with the muddy water discharge means 19 in which a plurality of convex portions 19a and concave portions 19b as shown in FIGS. The infiltration of muddy water and the like is more effectively suppressed by the swinging action of the muddy water discharging means 19 accompanying the rotation of 100. In particular, in the example shown in FIGS. 4A, 4B, and 4C, the groove-shaped portion or the blade-shaped portion is formed in a curved shape or a linear shape that is inclined. The air flow generated by the centrifugal action accompanying this further promotes the action of shaking off muddy water and the like. Further, the groove-shaped part or the blade-shaped part has a function of guiding muddy water or the like to the outside air side (the side opposite to the bearing space S). It is discharged efficiently.

  Since the opposed surfaces 170d and 18a are tapered surfaces whose diameter is increased toward the opposite side (vehicle body side) from the bearing space S, the opposed surfaces 170d and 18a are opposed to each other on the lower side of the shaft center L of the bearing seals 10 and 10A. The surface 170d is inclined downward toward the vehicle body. Therefore, even if muddy water or the like enters the space 300 surrounded by the first member 100 and the second member 200, the muddy water or the like is discharged to the outside air through the facing surface 170d inclined downward. Moreover, since the opposing surfaces 170d and 18a are parallel to each other, this discharge is made smoother. In particular, when the muddy water discharging means 19 is composed of a groove-shaped part or a blade-shaped part, these are also inclined toward the vehicle body side along the opposing surface (tapered surface) 18a. It is efficiently discharged along the groove shape portion or the blade shape portion. Furthermore, since the width d1 of the facing surface (tapered surface) 170d is larger than the width d2 of the facing surface (tapered surface) 18a, the facing surface 170d guides muddy water or the like that has entered the space 300 to the outside air side. The action becomes remarkable and the discharge function is more effectively exhibited. Thus, since the muddy water that has entered the space 300 is sequentially discharged, the amount of muddy water remaining in the space 300 can be extremely reduced. Therefore, wear or the like of the seal lips 17a due to mud water or the like entering the sliding contact portion of the seal lips 17a with the slinger 11 is less likely to occur, and the life of the bearing seals 10 and 10A can be extended. And since the function of preventing retention of muddy water or the like in the space portion 300 is effectively exhibited without increasing the sliding contact portion between the first member 100 and the second member 200, the rotational torque of the rotating side member is reduced. Can also be planned.

FIG. 6 shows another embodiment of the bearing sealing device according to the present invention, and FIGS. 7 to 9 show this modification. The bearing seals (bearing sealing devices) 10 </ b> B to 10 </ b> E shown in FIGS. 6 to 9 are common because the part forming the labyrinth structure with the elastic member 18 is one part of the core metal 14 constituting the second member 200. In the bearing seal 10B shown in FIG. 6, the cored bar 14 extends from the other end 15c of the cored bar cylindrical part 15 so as to extend along the vehicle body side end surface 2c of the outer ring 2, and from the outerd flange 15f. And a tapered portion 15g extending so as to expand toward the vehicle body side. The seal lip member 17 has three seal lips 17a, 17b, and 17c as in the above example, but the seal lip base portion 170 is a part of the inner surface 16a of the vehicle body side surface 16a and has an inner diameter. It is fixed to the metal core 14 so as to cover the entire side end portion 16b and the wheel side surface 16c. This seal lip base portion 170 has an annular protrusion 170g whose original shape is indicated by a two-dot chain line at the outer diameter portion of the portion covering the connecting portion between the cored bar cylindrical portion 15 and the inward flange portion 16. When the second member 200 is fitted to the outer ring 2, the annular protrusion 170 g is configured to be interposed in a compressed state, and muddy water or the like enters the metal fitting portion between the outer ring 2 and the cored bar 14. Even so, intrusion of muddy water or the like into the bearing space S is prevented.

In this embodiment, the elastic member 18 is formed in a lip shape whose diameter increases from the fixed base 180 fixed to the outer diameter side end 13b of the outward flange 13 in the slinger 11 toward the vehicle body. And the labyrinth structure r3 is formed of the taper-shaped part 15g extended from the cored bar cylindrical part 15 in the cored bar 14, and the lip-shaped elastic member 18. The opposing surfaces 15ga and 18a forming the labyrinth structure r3 are tapered surfaces that are parallel to each other and expand in diameter toward the vehicle body side (opposite the bearing space S), as described above. Further, the opposing surface (tapered surface) 18a is provided with a muddy water discharging means 19 as shown in FIGS. 4 and 5, and the width d1 of the tapered surface in the opposing surface 15ga is larger than the width d2 of the tapered surface in the opposing surface 18a. It is said that.
The bearing seal 10B having such a configuration also exhibits the same operations and effects as the above example. Since other configurations are the same as those in the above example, common portions are denoted by the same reference numerals and description thereof is omitted.

The bearing seal 10C shown in FIG. 7 differs from the bearing seal 10B shown in FIG. 6 only in the structure of the elastic member 18 and the structure of the seal lip member 17, except for the other structures. That is, the elastic member 18 extends so that the fixing base 180 extends to the wheel-side surface 13a of the outward flange 13 in the slinger 11 and from this portion to the vehicle-side surface 16a of the inward flange 16 of the core metal 14. It has a protruding seal lip 180b. Further, the seal lip member 17 does not have an axial lip and has two radial lips 17b and 17c. Therefore, the seal lip 180b of the elastic member 18 performs the same function instead of the axial lip 17a as shown in FIG.
Other configurations and operational effects are the same as those in the example of FIG.

The bearing seal 10D shown in FIG. 8 differs from the bearing seal 10B shown in FIG. 6 only in the structure of the elastic member 18 and the structure of the cored bar 14, but the other structures are the same. That is, the elastic member 18 has a lip shape as in the example of FIG. 6, but has a small extension width from the fixing base portion 180. Further, the cored bar 14 extends from the other end part 15c of the cored bar cylindrical part 15 so that the diameter of the cored bar 14 is increased toward the vehicle body side, and the taper-shaped part 15h continues to the vehicle body side of the outer ring 2 continuously. And an outward flange 15i extending along the end face 2c. In the bearing seal 10D of this example, a labyrinth structure r4 is formed by the tapered portion 15h extending from the core metal cylindrical portion 15 of the core metal 14 and the lip-shaped elastic member 18. The facing surfaces 15ha and 18a constituting the labyrinth structure r4 are tapered surfaces which are parallel to each other and expand in diameter toward the vehicle body side (opposite to the bearing space S), as described above. Further, the opposing surface (tapered surface) 18a is provided with a muddy water discharging means 19 as shown in FIGS. 4 and 5, and the width d1 of the tapered surface in the opposing surface 15ha is larger than the width d2 of the tapered surface in the opposing surface 18a. It is said that. Furthermore, the minimum gap d3 between the facing surface 15ha as the fixed side member and the muddy water discharge means 19 (projection 19a) is set to 0.1 to 1.00 mm.
The bearing seal 10D having such a configuration also exhibits the same operations and effects as the bearing seals shown in the above examples. Since other configurations are the same as the example shown in FIG. 6, the same reference numerals are given to common portions, and the description thereof is omitted.

The bearing seal 10E shown in FIG. 9 differs from the bearing seal 10D shown in FIG. 8 only in the structure of the elastic member 18 and the structure of the seal lip member 17, but the other structures are the same. That is, the elastic member 18 extends so that the fixing base 180 elastically contacts the wheel-side surface 13a of the outward flange 13 of the slinger 11 and the vehicle-side surface 16a of the inward flange 16 of the core metal 14 from this portion. It has a protruding seal lip 180b. Further, the seal lip member 17 does not have an axial lip and has two radial lips 17b and 17c. Therefore, as in the example shown in FIG. 7, the seal lip 180b of the elastic member 18 performs the same function instead of the axial lip.
Since other configurations and operational effects are the same as those in the example of FIG. 8, common portions are denoted by the same reference numerals and description thereof is omitted.

FIG. 10 shows still another embodiment of the bearing sealing device according to the present invention, and FIGS. 11 to 13 show this modification. The bearing seals (bearing sealing devices) 10F, 10G, 10H, and 10J shown in FIGS. 10 to 13 are common because the part that forms the labyrinth structure with the elastic member 18 is one part of the outer ring 2 that constitutes the stationary member. To do. That is, the corner portion 2d of the inner diameter surface 2b and the vehicle body-side end surface 2c of the outer ring 2 is chamfered, the corner portion 2d of the chamfered shape is the opposing surface to form a resilient member 18 and the labyrinth structure r5. The opposing surfaces (corner portions) 2d and 18a that form the labyrinth structure r5 are tapered surfaces that are parallel to each other and expand in diameter toward the vehicle body. Further, the opposing surface (tapered surface) 18a is provided with a muddy water discharging means 19 as shown in FIGS. 4 and 5, and the width d1 of the tapered surface at the opposing surface (corner) 2d is equal to the tapered surface of the opposing surface 18a. The width is greater than d2. Furthermore, the minimum gap d3 between the facing surface 2d as the fixed side member and the muddy water discharge means 19 (convex portion 19a) is set to 0.1 to 1.00 mm.

In the bearing seal 10F shown in FIG. 10, the seal lip member 17 is configured similarly to the bearing seals 10B and 10D shown in FIGS. Therefore, the same code | symbol is attached | subjected to the part which is common with these, and the description is abbreviate | omitted. The elastic member 18 is integrally fixed to the outer diameter side end 13b of the outward flange 13 of the slinger 11 by a fixing base 180, and is formed so as to extend from the fixing base 180 substantially in the outer diameter direction. The end surface is a facing surface 18a.
The bearing seal 10F having such a configuration also has the same operations and effects as the bearing seals of the above examples.

In the bearing seal 10G shown in FIG. 11, the seal lip member 17 is configured similarly to the bearing seals 10C and 10E shown in FIGS. Therefore, the same code | symbol is attached | subjected to the part which is common with these, and the description is abbreviate | omitted. The elastic member 18 is integrally fixed to the outer diameter side end 13b of the outward flange 13 of the slinger 11 by a fixing base 180, and is formed so as to extend from the fixing base 180 substantially in the outer diameter direction. The end surface is a facing surface 18a. In the case of this example, the protruding width of the outward flange 13 in the slinger 11 is shorter than the example shown in FIG. 10, and the extending width of the elastic member 18 is larger than the example shown in FIG.
The bearing seal 10G having such a configuration also has the same operations and effects as the bearing seals of the above examples.

  In the bearing seal 10H shown in FIG. 12, the slinger 11 has a slinger cylindrical portion 12 fitted to the outer diameter surface 4b of the inner ring member 4 and an outer diameter from one end portion 12a of the slinger cylindrical portion 12 in the same manner as described above. It consists of the outward flange 13 extended to the side. However, the slinger 11 of this example is fitted to the inner ring member 4 in the opposite direction to the above examples. That is, the one end portion 12a is an end portion on the wheel side. The cored bar 14 includes a cored bar cylindrical part 15 that is shorter than the above examples, and an inward flange part 16 that extends to the inner diameter side from one end part (the vehicle body side end part in the illustrated example) 15a of the cored bar cylindrical part 15. It consists of. The fixing base 180 of the elastic member 18 is fixed to the outer diameter side end 13b of the outward flange 13 in the slinger 11, and the elastic member 18 extends straight from the fixing base 180 in the outer diameter direction, and further toward the vehicle body side. It is formed in a lip shape extending so as to expand the diameter. The outer diameter side surface of the lip-shaped elastic member 18 is a facing surface (tapered surface) 2d that is a corner of the outer ring 2 and a facing surface (tapered surface) 18a that forms the labyrinth structure r5.

Further, the seal lip base portion 170 of the seal lip member 17 covers the vehicle body side surface 16a of the inward flange portion 16 from the outer diameter surface 15d of the core metal cylindrical portion 15 of the core metal 14, and wraps around the inner diameter side end portion 16b. And fixed to the metal core 14 so as to reach the wheel-side surface 16c. From the seal lip base 170, there are two seal lips, an axial lip 17 a that elastically contacts the wheel-side surface 13 a of the outward flange 13 of the slinger 11, and a radial lip 17 b that elastically contacts the outer diameter surface 4 b of the inner ring member 4. It has been extended. A portion of the seal lip base portion 170 covering the outer diameter surface 15d of the cored bar cylindrical portion 15 is an annular thick portion 170h enlarged in the outer diameter direction. The metal core 14 having such a seal lip member 17 is elastically mounted between the outer ring 2 and the inner ring member 4. In this mounted state, the radial lip 17b is elastically deformed in the outer diameter direction, is elastically contacted with the outer diameter surface 4b of the inner ring member 4, and the thick wall portion 170h is a circumferential groove formed on the inner diameter surface 2b of the outer ring 2. 2e is fitted with elastic deformation (the two-dot chain line indicates the original shape) and attached to the outer ring 2 integrally. As a result, the cored bar 14 and the seal lip member 17 are the second member 200 that constitutes a part of the stationary member, as described above. The slinger 11 is integrally attached to the inner ring member 4 by fitting the slinger cylindrical portion 12 together with the elastic member 18 to the outer diameter surface 4 b of the inner ring member 4. The slinger 11 and the elastic member 18 are the first member 100 that constitutes a part of the rotation side member, as described above. The axial lip 17a elastically slides on the wheel-side surface 13a of the outward flange 13 in the slinger 11 as the first member 100 constituting a part of the rotation-side member rotates about the axis L (see FIG. 1). Further, the radial lip 17b is in sliding contact with the outer diameter surface 4b of the inner ring member 4 elastically.
The bearing seal 10H having such a configuration also has the same operations and effects as the bearing seals of the above examples.

  In the bearing seal 10J shown in FIG. 13, the slinger 11 is made of an annular disk member. The fixed base portion 180 of the elastic member 18 covers the vehicle body side surface (surface opposite to the bearing space S) 11b from the outer diameter side end portion 11a of the slinger 11, and the wheel side surface (from the inner diameter side end portion 11c). The surface of the bearing space S is fixed to the slinger 11 so as to reach the surface 11d. And the part which covers the inner diameter side edge part 11c in the adhering base part 180 is made into the thick part 180c expanded in the inner diameter direction. Further, a lip-shaped elastic member 18 substantially the same as the example of FIG. 12 is extended from the outer diameter side end portion of the fixing base portion 180. The outer diameter side surface of the lip-shaped elastic member 18 is an opposing surface (tapered surface) 18a that forms the labyrinth structure r5 with the opposing surface (tapered surface) 2d of the outer ring 2. On the other hand, the cored bar 14 includes a cylindrical portion 15A and an outward flange portion 16A extending in the outer diameter direction from one end portion (vehicle body side end portion in the illustrated example) 15Aa of the cylindrical portion 15A.

The seal lip base portion 170 of the seal lip member 17 covers the vehicle body side surface 16Aa of the outward flange portion 16A from the inner diameter surface 15Ab of the cylindrical portion 15A of the core metal 14, and wraps around the outer diameter side end portion 16Ab on the wheel side. The metal core 14 is fixed so as to reach the surface 16Ac. From the seal lip base portion 170, two seal lips are extended: an axial lip 17 a that elastically contacts the wheel-side surface 11 d of the slinger 11, and a radial lip 17 b that elastically contacts the outer diameter surface 4 b of the inner ring member 4. . A portion of the seal lip base portion 170 that wraps around the outer diameter side end portion 16Ab of the outward flange portion 16A is an annular thick portion 170h that is enlarged in the outer diameter direction. The metal core 14 having such a seal lip member 17 is elastically mounted between the outer ring 2 and the inner ring member 4. In this mounted state, the radial lip 17b is elastically deformed in the outer diameter direction, is elastically contacted with the outer diameter surface 4b of the inner ring member 4, and the thick wall portion 170h is a circumferential groove formed on the inner diameter surface 2b of the outer ring 2. 2e is fitted with elastic deformation (the two-dot chain line indicates the original shape) and attached to the outer ring 2 integrally. As a result, the cored bar 14 and the seal lip member 17 are the second member 200 that constitutes a part of the stationary member, as described above. The slinger 11 is fitted together with the thick portion 180c of the elastic member 18 into the circumferential groove 4c formed on the outer diameter surface 4b of the inner ring member 4 with elastic deformation (the two-dot chain line indicates the original shape). It is attached to the member 4 integrally. The slinger 11 and the elastic member 18 are the first member 100 that constitutes a part of the rotation side member, as described above. The axial lip 17a is elastically slidably in contact with the wheel-side surface 11d of the slinger 11 along with the rotation around the axis L (see FIG. 1) of the first member 100 constituting a part of the rotation side member. The lip 17 b elastically slides on the outer diameter surface 4 b of the inner ring member 4.
The bearing seal 10J having such a configuration also has the same operations and effects as the bearing seals of the above examples.

  FIG. 14 shows still another embodiment of the bearing sealing device according to the present invention. In the bearing seal (bearing sealing device) 10K of this embodiment, the elastic member 18 forms a part of an annular magnet 20 in which an elastomer such as rubber or elastic resin containing magnetic powder is molded integrally with the slinger 11. It is configured as follows. The annular magnet 20 is integrally fixed to a surface (surface opposite to the bearing space S) 13c of the outward flange 13 of the slinger 11 by vulcanization molding, and a part of the annular magnet 20 is outside the outward flange 13. It goes around the diameter side end portion 13b to reach the wheel side surface (the surface on the bearing space S side) 13a, and this wraparound portion is the elastic member 18. In this way, the annular magnet 20, part of which is the elastic member 18, and the slinger 11 are the first member 100 that constitutes a part of the rotation side member. A large number of north and south poles (not shown) are alternately magnetized along the circumferential direction on the surface 20a of the annular magnet 20 on the vehicle body side to form a magnetic encoder. A magnetic sensor 21 is fixed on the vehicle body side so as to face the annular magnet (magnetic encoder) 20, and the wheel rotation detection device 22 detects a magnetic change of the annular magnet 20 due to rotation by the magnetic sensor 21 and the annular magnet 20. Is configured.

On the other hand, the 2nd member 200 which comprises a part of fixed side member is provided with the metal core 14 and the seal lip member 17 fixed to this similarly to the example shown in FIG. Therefore, about these structures, the same code | symbol is attached | subjected to a common part and the description is abbreviate | omitted. Also in the bearing seal 10K of this example, the labyrinth structure r6 is formed by the portion of the seal lip member 17 that covers the core metal cylindrical portion 15 of the seal lip base 170 and the elastic member 18, and each of the two forming the labyrinth structure r6. The opposed surfaces 170d and 18a are tapered surfaces that are parallel to each other and expand in diameter toward the opposite side of the bearing space S. The taper surface widths d1 and d2 of the opposing surfaces 170d and 18a forming the taper surfaces are set such that the taper surface width d1 of the former counter surface 170d is larger than the taper surface width d2 of the latter counter surface 18a. And the muddy water discharge means 19 comprised by the opposing surface (taper surface) 18a of the elastic member 18 as shown in FIG.4 and FIG.5 by the convex part 19a and the recessed part 19b is provided. Further, the minimum gap d3 between the facing surface 170d as the fixed side member and the muddy water discharging means 19 (the convex portion 19a) is set to 0.1 to 1.00 mm as described above.
The bearing seal 10K having such a configuration also has the same operations and effects as the above example. Since other configurations are the same as those in the above example, common portions are denoted by the same reference numerals, and descriptions of operations and effects thereof are omitted.

FIG. 15 shows still another embodiment of the bearing sealing device according to the present invention. In the bearing seal (bearing sealing device) 10L of this embodiment, the first member 100 constituting a part of the rotation side member does not have the elastic member as in the above example, and includes only the slinger (metal ring) 11. Yes.
On the other hand, the 2nd member 200 which comprises a part of fixed side member is provided with the metal core 14 and the seal lip member 17 fixed to this similarly to the example shown in FIG. A muddy water discharge means 19 is provided on the seal lip member 17. More specifically, the outward flange 13 in the slinger 11 has a bent portion 13d facing the vehicle body at the outer diameter side end, and the outer diameter surface 13e of the bent portion 13d and the seal lip member 17 are sealed. The labyrinth structure r7 is formed by the portion of the lip base 170 covering the cored bar cylindrical portion 15, and the opposing surfaces 170d and 13e (the outer diameter surfaces of the slinger 11) of the labyrinth structure r7 are parallel to each other. And it is set as the taper surface which diameter-expands toward the opposite side to the bearing space S. As shown in FIG. The taper surface widths d1 and d2 of the opposing surfaces 170d and 13e forming the tapered surfaces are set such that the taper surface width d1 of the former counter surface 170d is larger than the taper surface width d2 of the latter counter surface 13e. Further, a muddy water discharge means 19 constituted by a convex portion 19a and a concave portion 19b as shown in FIGS. 4 and 5 is provided on the opposing surface (tapered surface) 170d of the seal lip member 17. Further, the minimum gap d3 between the facing surface 13e as the rotation side member and the muddy water discharge means 19 (projection 19a) is set to 0.1 to 1.00 mm as described above.

  Also in the bearing seal 10L of this embodiment, the opposing surfaces 170d and 13e are parallel to each other, and are tapered surfaces that increase in diameter toward the opposite side of the bearing space S. There are effects and effects. Further, in the embodiment, the muddy water discharging means 19 is provided on the seal lip member 17 that is a stationary side member, but along the muddy water discharging means 19 by an air flow generated with the rotation of the slinger 11 that is a rotating side member. The muddy water is discharged efficiently. In each of the above examples, the muddy water discharging means 19 is provided on the rotating side member. However, in each of these examples, the muddy water discharging means 19 may be provided on the fixed side member instead of the rotating side member. Since other configurations are the same as those in the above example, common portions are denoted by the same reference numerals, and descriptions of operations and effects thereof are omitted.

In the embodiment described above, the bearing sealing device of the present invention is embodied in the vehicle body side bearing seal 10 in FIG. 1, but other than the example shown in FIG. 14, it is embodied in the wheel side bearing seal 9. It is also possible to make it. Further, the bearing device to which the bearing sealing device according to the present invention is applied is not limited to the bearing device 1 for driving wheels as shown in FIG. 1, and may be a bearing device for driven wheels, or an automobile. The bearing device is not limited to the above, and is a bearing device in which the rotating side member is supported so as to be coaxially rotatable with respect to the fixed side member, and is a bearing device for other industrial machines that is subject to an attack such as muddy water. May be. Further, the structure and number of seal lips are not limited to those shown in the drawings.
Further, the structure of the opposing surface constituting the labyrinth structure is not limited to the illustrated one, and other structures may be used as long as they are tapered surfaces that are parallel to each other and expand toward the opposite side to the bearing space. It can be adopted. Further, the projections and recesses constituting the muddy water discharging means are not limited to the illustrated structure, and other structures can be adopted, and the muddy water discharging means is repeatedly formed along the circumferential direction as illustrated. It may be composed of a structure other than the convex and concave portions. In addition, in the embodiment, the inner ring is the rotation side member and the outer ring is the fixed side member, but the inner ring may be the fixed side member and the outer ring may be the rotation side member.

1 Bearing device 2 Outer ring (fixed side member)
3 Hub wheel (rotary member)
4 Inner ring member (rotating side member)
5 Inner ring (rotary member)
10, 10A to 10H, 10J to 10L Bearing seal (bearing sealing device)
11 Slinger (metal ring)
14 Core 17 Seal lip member 17a, 17b, 17c Seal lip 18 Elastic member 18a Opposing surface (tapered surface)
170d, 15ga, 15ha, 2d, facing surface (tapered surface)
19 Muddy water discharge means 19a Convex part 19b Concave part 100 1st member (a part of rotation side member)
200 Second member (part of fixed member)
d1 Width of tapered surface of fixed side member d2 Width of tapered surface of elastic member d3 Minimum gap between opposed surfaces r, r1 to r7 Labyrinth structure L Axis center

Claims (10)

A bearing sealing device mounted on an axial end of an annular bearing space in a bearing device in which a rotation side member is supported so as to be coaxially rotatable with respect to a fixed side member,
A first member that comprises a metal ring that is integrally attached to the rotating side member and constitutes a part of the rotating side member; a metal core that is integrally attached to the stationary side member; and the metal that is fixed to the metal core A seal lip member having an elastic seal lip that elastically contacts the ring, and a second member constituting a part of the fixed side member,
The rotating side member and the stationary side member form a labyrinth structure at a portion opposite to the bearing space,
Respective facing surfaces forming the labyrinth structure in the rotating side member and the stationary side member have a tapered surface that is parallel to each other and expands toward the opposite side to the bearing space,
An elastic member is fixed to the radial end portion of the metal ring via a fixing base, and the elastic member is formed to protrude from the fixing base to the side opposite to the bearing space. The fixed side members each have the tapered surface that forms the labyrinth structure,
One of the tapered surfaces is provided with a muddy water discharging means. The bearing sealing device according to claim 1 ,
The bearing sealing device, wherein the muddy water discharging means is provided on a tapered surface of the elastic member. The bearing sealing device according to claim 1,
The bearing sealing device, wherein the elastic member of the rotation side member and the seal lip member each have the tapered surface forming the labyrinth structure. The bearing sealing device according to claim 3 ,
A bearing sealing device, wherein the muddy water discharge means is provided on a tapered surface of the seal lip member. The bearing sealing device according to any one of claims 1 to 4 ,
The width of the taper surface of the fixed side member is larger than the width of the taper surface of the rotation side member. The bearing sealing device according to any one of claims 1 to 5 ,
The bearing sealing device, wherein the muddy water discharging means includes a convex portion and a concave portion that are repeatedly formed along the circumferential direction on any one of the tapered surfaces. The bearing sealing device according to claim 6 ,
2. The bearing sealing device according to claim 1, wherein the concave portion of the muddy water discharging means is composed of a plurality of groove-shaped portions, and the convex portion is composed of a portion between the groove-shaped portions. The bearing sealing device according to claim 6 ,
The bearing sealing device, wherein the muddy water discharging means has a plurality of blade-shaped portions, and the recessed portion has a portion between the blade-shaped portions. The bearing sealing device according to claim 6 ,
2. The bearing sealing device according to claim 1, wherein the muddy water discharging means has a plurality of convex portions, and the concave portion has a valley-shaped portion between the convex portions. The bearing sealing device according to any one of claims 1 to 9 ,
A bearing sealing device, wherein a minimum gap between the muddy water discharging means and the other tapered surface facing the muddy water discharging means is set to 0.1 to 1.00 mm.

Images