JP5708403B2 - Sealing device for bearing - Google Patents

Description

  The present invention relates to a bearing sealing device that seals the inside of a bearing from the outside of the bearing.

  2. Description of the Related Art Conventionally, bearings that rotatably support an axle of a vehicle such as an automobile or a railroad have been used (see, for example, Patent Document 1). Various bearing sealing devices are provided for sealing the inside of the bearing (specifically, the bearing internal space) partitioned between the outside of the bearing.

  As an example, FIG. 6 (a) shows a bearing unit for a drive wheel, and the bearing unit is fixed to a vehicle body side component and is constantly maintained in a non-rotating state (for example, A stationary ring (outer ring) 2) and the other raceway ring (for example, a rotating ring (inner ring)) that is disposed facing the inner side of the stationary ring (outer ring) 2 and that is connected to the wheel side component and rotates together with the wheel. 4) and a plurality of rolling elements 6, 8 that are rotatably incorporated in a double row (for example, two rows) between the stationary wheel 2 and the rotating wheel 4 that rotate relative to each other about a single rotation axis Ax. And. In addition, as the rolling elements 6 and 8, “balls” are illustrated in the drawings, but “rollers” may be applied depending on the purpose and environment of use of the bearing unit.

  The stationary ring (outer ring) 2 has a hollow cylindrical shape and is arranged so as to cover the outer periphery of the rotating ring (inner ring) 4. In this case, between the stationary wheel 2 and the rotating wheel 4, the inside of the bearing of the bearing unit (that is, the annular bearing inner space defined between the stationary wheel 2 and the rotating wheel 4) is disposed on both axial sides. A bearing sealing device (wheel side lip seal 10a, vehicle body side pack seal 10b) is provided for sealing from the side. The axial direction refers to a direction parallel to the rotation axis Ax.

  The stationary ring (outer ring) 2 is integrally formed with a fixing flange 2a that projects radially outward from the outer peripheral side thereof. In this case, the stationary wheel 2 can be fixed to, for example, a knuckle (not shown) by inserting a fixing bolt (not shown) into the fixing hole 2b of the fixing flange 2a and fastening it to the vehicle body side component. .

  On the other hand, the rotating wheel (inner ring) 4 is provided with a hub 12 that rotates together with supporting the wheel-side components and has a hollow cylindrical shape. The hub 12 is provided with, for example, a disc wheel (not shown). The hub flange 12a is fixedly provided. The hub flange 12a extends radially outward (outward in the radial direction of the hub 12) beyond the stationary ring (outer ring) 2, and in the vicinity of the extended edge at a predetermined interval along the circumferential direction. A plurality of arranged hub bolts 14 are provided. The radial direction refers to a direction orthogonal to the rotation axis Ax.

  Here, by inserting a plurality of hub bolts 14 into respective bolt holes (not shown) formed in the disc wheel and tightening with hub nuts (not shown), the disc wheel is positioned and fixed with respect to the hub flange 12a. can do. At this time, the radial positioning of the wheel-side component is performed by the pilot portion 12d protruding from the wheel side of the hub 12.

  Further, the hub 12 has a fitting surface 4n formed at the end of the vehicle body on the outer peripheral surface 4m thereof, and the fitting surface 4n has an annular rotating wheel constituting body 16 (a rotating wheel (inner ring together with the hub 12)). ) 4) can be fitted (press-fitted). In this case, for example, in a state where the rolling elements 6 and 8 are held by the cage 18 between the stationary wheel 2 and the rotating wheel 4, the rotating wheel component 16 is moved to the step portion 12b formed on the fitting surface 4n. After the fitting, the caulking region 12c at the end of the hub 12 on the vehicle body side is plastically deformed, and the caulking region 12c is caulked (closely adhered) along the peripheral end 16s of the rotating wheel component 16. The rotating wheel component 16 can be fixed to the hub 12.

  At this time, a predetermined preload is applied to the bearing unit, and in this state, the rolling elements 6 and 8 form a predetermined contact angle with each other and each raceway groove ( The stationary raceway groove 2s and the rotary raceway groove 4s) are in contact with each other and are rotatably incorporated. In this case, an action line (not shown) connecting the two contact points is orthogonal to the raceway grooves 2s and 4s, passes through the centers of the rolling elements 6 and 8, and is on one point on the center line of the bearing unit ( At the point of action). This constitutes a rear combination (DB) bearing.

  In such a bearing configuration, all of the force acting on the wheel during vehicle travel is transmitted from the disk wheel to the knuckle through the bearing unit. At this time, various loads (radial load, axial load) are applied to the bearing unit. Load, moment load, etc.). However, since the bearing unit is a back combination (DB) bearing as described above, high rigidity is maintained against various loads.

  Further, in the bearing sealing device provided in the bearing unit described above, the lip seal 10a is fixed to the fixed surface 2n-1 on the wheel side of the stationary wheel (outer ring) 2, and the sliding of the rotating wheel 4 (hub 12). It is slidably positioned with respect to the surface 4n-1. On the other hand, the pack seal 10b is slidably positioned between the stationary surface 2n-2 on the vehicle body side of the stationary wheel (outer ring) 2 and the other raceway ring 4 (rotating wheel component 16). Specifically, the rotating wheel component 16 is formed with a fitting surface 16m facing the fixed surface 2n-2 of the stationary wheel (outer ring) 2, and the pack seal 10b is connected to the fitting surface 16m. It is positioned in a state of being press-fitted and fitted between the fixed surface 2n-2.

Here, the pack seal 10b will be described.
As shown in FIG. 6 (b), the pack seal 10b is fitted (press-fitted) to the fixed surface 2n-2 on the vehicle body side of one of the race rings (stationary ring (outer ring) 2), and between the race rings (stationary ring). The seal body 20 extending so as to cover the inside (space) of the bearing partitioned between (2) and the rotating wheel 4) and the fitting surface 16m of the other race ring 4 (rotating ring component 16). A slinger 24 that is (press-fitted) and extends so as to cover the inside (space) of the bearing defined between the raceway rings (between the stationary wheel 2 and the rotating wheel 4).

  Here, the seal body 20 is configured by vulcanizing the seal material 28 on the inner peripheral surface (surface facing the slinger 24) of the mandrel 26. The seal material 28 includes a plurality of (for example, three) seal materials. The seal lips 28a, 28b, and 28c are integrally formed. The mandrel 26 is a hollow cylindrical portion 26a having a hollow cylindrical shape that is fitted (press-fitted) to the fixed surface 2n-2, and the hollow cylindrical portion 26a is directed toward the rotating wheel component 16 (fitting surface 16m). An annular folded portion 26b having a hollow disk shape that is folded back and extends so as to cover the inside (space) of the bearing is provided.

  On the other hand, the slinger 24 is positioned closer to the bearing outer side than the seal body 20, and includes a slinger wall portion 24a having a hollow disk shape extending in the radial direction so as to cover the inside (space) of the bearing, and the slinger wall portion 24a. A slinger base portion 24b having a hollow cylindrical shape extending in the axial direction toward the inside (space) of the bearing and fitted (press-fitted) to the fitting surface 16m of the other race ring 4 (rotating ring component 16). ing. Of the three seal lips 28a, 28b, and 28c, one seal lip 28a is in sliding contact with the slinger wall portion 24a, and the remaining two seal lips 28b and 28c are in sliding contact with the slinger base portion 24b.

  According to such a pack seal 10b, the three seal lips 28a, 28b, and 28c are slinger 24 while the bearing is rotating (while the stationary wheel 2 and the rotating wheel 4 are relatively rotated) or while the bearing is not rotating. Is always in sliding contact. As a result, the inside of the bearing (space) can be sealed from the outside of the bearing, so that foreign matter (eg, water, dust) can be prevented from entering the inside of the bearing (space) and leakage of the lubricant to the outside of the bearing can be prevented. Can be planned. As the sealing material 28, for example, an elastic material such as rubber or elastomer can be applied, and as a method of adding the sealing material 28 to the inner peripheral surface of the mandrel 26, for example, by baking or vulcanization adhesion Add it.

  Further, the pack seal 10b described above is fitted (press-fit) between the fitting surface 16m of the rotating wheel constituting body 16 and the fixed surface 2n-2 of the stationary wheel (outer ring) 2; Depending on the (press-fit) force, for example, the fitting surfaces of the mandrel 26 (hollow cylindrical portion 26a) and the fixed surface 2n-2 may be damaged. Then, depending on the degree of damage, the sealed state inside the bearing (space) is lowered.

  Therefore, as a sealing measure, for example, as shown in FIG. 6 (b), a seal member 28 is attached to the end 26c of the mandrel 26 (hollow cylindrical portion 26a) (the end opposite to the annular folded portion 26b). A method of forming the nose casket 30 is known. The nose casket 30 is formed by turning a sealing material 28 so as to cover the vehicle body side end portion 26c of the mandrel 26, and a part thereof is bulged toward the stationary ring (outer ring) 2 side. . Thereby, the maintenance improvement of the sealing performance with respect to the bearing interior (space) is achieved.

JP 2010-105475 A

  By the way, when the bearing unit described above is applied to a larger vehicle, one bearing ring (for example, a stationary ring (outer ring) 2) and the other bearing ring (for example, a rotating wheel (for example, a rotating wheel)) that rotate relative to each other about the rotation axis Ax. The diameter of the inner ring 4) is increased, but the outer diameter of the bearing (particularly, the outer diameter of the stationary ring (outer ring) 2) increases in accordance with the extent of the increase.

  Here, assuming that a moment load is applied to the bearing unit due to the force applied to the wheels during vehicle travel as described above, the above-described bearing unit is configured depending on the magnitude of the magnitude of the moment load. In some cases, the stationary wheel (outer ring) 2 and the rotating wheel (inner ring) 4 are relatively inclined about the rotation axis Ax.

  In this case, since the relative inclination angle between the stationary wheel (outer ring) 2 and the rotating wheel (inner ring) 4 affects the maneuverability and running stability of the vehicle, a large rigid bearing unit is used. Whether the vehicle is a large vehicle or a small vehicle in which a small bearing unit with low rigidity is used, the inclination angle is substantially the same.

  However, even at the same inclination angle, a change in tightening margin due to the inclination differs between a large (large diameter) seal used for a large bearing unit and a small (small diameter) seal used for a small bearing unit.

  In addition, in order to ensure the sealing performance, it is necessary to give a large tightening allowance to a large-diameter seal with a large tightening allowance change. It will be heavy.

  The present invention has been made to solve such a problem, and the object thereof is to mitigate a change in the seal lip tightening allowance due to the generation of an inclination angle, thereby suppressing an increase in seal tightening allowance and sealing performance. An object of the present invention is to provide a bearing sealing device that can reduce the torque of a seal without lowering the torque. In particular, this technique is effective for large seals used in bearing units for large vehicles.

In order to achieve such an object, the present invention is a bearing sealing device that is provided between bearing rings arranged to face each other so as to be relatively rotatable, and seals the inside of the bearing partitioned between the bearing rings. The first seal body that is fitted in one of the bearing rings and continuously provided along the circumferential direction so as to cover the inside of the bearing, and the other seal ring is fitted and covers the inside of the bearing. A first slinger provided continuously along the circumferential direction, and interposed between the first seal body and the first slinger so as to be relatively rotatable, and continuous along the circumferential direction so as to cover the inside of the bearing. The intermediate seal structure is provided with a second slinger that is slidably contacted with the seal lip formed on the first seal body, and a seal lip that is slidably contacted with the first slinger. It is possible to integrate the second seal main body It is.
In the present invention, a plurality of seal lips are formed between the first seal body and the second slinger in sliding contact with at least two directions of the axial direction and the radial direction. A plurality of seal lips are formed in sliding contact with at least two directions of the axial direction and the radial direction.
In the present invention, the first slinger is positioned closer to the outside of the bearing than the second seal body, and includes a first slinger wall portion having a hollow disk shape extending so as to cover the inside of the bearing, A first slinger base portion having a hollow cylindrical shape extending from the slinger wall toward the inside of the bearing, and the second slinger is positioned closer to the outside of the bearing than the first seal body. A second slinger wall portion that has a hollow disc shape extending so as to cover the inner surface, and a second slinger base portion that has a hollow cylindrical shape that extends from the second slinger wall portion toward the inside of the bearing. Yes.
In the present invention, the intermediate seal structure includes the sliding contact force of the plurality of seal lips between the first seal body and the second slinger, and the plurality of seal lips between the second seal body and the first slinger. It is maintained in a state where it is supported at a position balanced with the sliding contact force.

  According to the present invention, it is possible to suppress an increase in seal tightening allowance by reducing a change in seal lip tightening allowance accompanying the generation of an inclination angle, and to reduce the seal torque without degrading the sealing performance. The bearing sealing device can be realized. In particular, this technique is effective for large seals used in bearing units for large vehicles.

(a) is sectional drawing which expands partially the structure of the bearing unit to which the sealing device for bearings concerning one Embodiment of this invention was applied, (b) is a bearing shown by the figure (a). Sectional drawing which expands and shows a part of the structure of the sealing device for a machine. (a) is sectional drawing which expands and partially shows the structure of the sealing device for bearings which concerns on the modification of this invention, (b) expands partially the structure of the sealing device for bearings which concerns on the modification of this invention FIG. (a) is sectional drawing which expands and partially shows the structure of the sealing device for bearings which concerns on the modification of this invention, (b) expands partially the structure of the sealing device for bearings which concerns on the modification of this invention FIG. (a) is sectional drawing which expands and partially shows the structure of the sealing device for bearings which concerns on the modification of this invention, (b) expands partially the structure of the sealing device for bearings which concerns on the modification of this invention FIG. (a) is sectional drawing which expands and partially shows the structure of the sealing device for bearings which concerns on the modification of this invention, (b) expands partially the structure of the sealing device for bearings which concerns on the modification of this invention FIG. (a) is sectional drawing which shows the structure of the bearing unit to which the sealing device for bearings was applied, (b) expanded partially the structure of the conventional bearing sealing device shown to the same figure (a). FIG.

Hereinafter, a bearing sealing device according to an embodiment of the present invention will be described with reference to the accompanying drawings.
As shown in FIGS. 1 (a) and 1 (b), the bearing sealing device (specifically, the pack seal 10b on the vehicle body side) of the present embodiment has one bearing ring (for example, a stationary ring (outer ring) 2). ), And is fitted to the first seal body 20 provided continuously along the circumferential direction so as to cover the inside of the bearing, and the other race ring (for example, the rotating ring (inner ring) 4), The first slinger 24 provided continuously along the circumferential direction so as to cover the inside of the bearing, and the first seal body 20 and the first slinger 24 are interposed (inserted) so as to be relatively rotatable. And an intermediate seal structure provided continuously along the circumferential direction so as to cover the inside of the bearing.

  Here, the first seal body 20 is configured by vulcanizing the first seal material 28 on the inner peripheral surface of the first mandrel 26 (the surface facing the second slinger 22s described later). The first sealing material 28 is integrally formed with a plurality of (for example, three) first sealing lips 28a, 28b, and 28c. The first mandrel 26 includes a first hollow cylindrical portion 26a having a hollow cylindrical shape that is fitted (press-fitted) to the stationary surface 2n-2 on the vehicle body side of the stationary ring (outer ring) 2, and a first hollow cylindrical portion 26a. A first annular folded portion 26b having a hollow disk shape that is folded back from the hollow cylindrical portion 26a toward the rotating wheel constituting body 16 (fitting surface 16m) and extends to cover the bearing interior (space). ing.

  On the other hand, the first slinger 24 is positioned closer to the outside of the bearing than a second seal body 22t, which will be described later, and has a hollow disk shape extending in the radial direction so as to cover the inside (space) of the bearing. The slinger wall 24a and the first slinger wall 24a extend in the axial direction toward the inside of the bearing (space), and are fitted (press-fit) to the fitting surface 16m of the other race ring 4 (rotating ring component 16). A first slinger base portion 24b having a hollow cylindrical shape.

  The intermediate seal structure includes a plurality of seal lips 28 a, 28 b, 28 c integrally formed with the first seal body 20, and a plurality of seal lips 32 a slidably in contact with the first slinger 24. , 32b, 32c are integrated with a second seal body 22t formed integrally.

  Here, the second seal body 22t is configured by vulcanizing the second seal material 32 on the inner peripheral surface of the second mandrel 34 (the surface facing the first slinger 24), A plurality of (for example, three) second seal lips 32 a, 32 b, and 32 c are integrally formed on the second seal material 32. The second mandrel 34 includes a second hollow cylindrical portion 34a having a hollow cylindrical shape that also serves as a second slinger base portion 22b of a second slinger 22s described later, and a second hollow cylindrical portion 34a. A second annular folded portion 34b having a hollow disk shape that is folded back toward the rotating wheel constituting body 16 (fitting surface 16m) and extends so as to cover the inside (space) of the bearing is provided.

  On the other hand, the second slinger 22s is positioned closer to the outside of the bearing than the first seal body 20, and a second slinger wall having a hollow disk shape extending in the radial direction so as to cover the inside (space) of the bearing. Portion 22a and a second slinger base portion 22b having a hollow cylindrical shape extending in the axial direction from the second slinger wall portion 22a toward the inside of the bearing (space) (the second of the second mandrel 34 described above) A hollow cylindrical portion 34a).

  As the first and second sealing materials 28 and 32, for example, an elastic material such as rubber or elastomer can be applied, and the sealing materials 28 and 32 are used as the first and second cores 26. , 34 may be added by, for example, baking or vulcanization adhesion.

  In this case, the plurality of (for example, three) first seal lips 28a, 28b, and 28c integrally formed with the first seal body 20 are at least in the axial direction and the radial direction with respect to the second slinger 22s. It is preferable to make it slidably contact in two directions. In the drawing, as an example, of the three first seal lips 28a, 28b, 28c, one seal lip 28a is brought into sliding contact with the second slinger wall portion 22a in the axial direction, and the remaining two seal lips 28b. 28c are in sliding contact with the second slinger base 22b in the radial direction.

  In addition, a plurality of (for example, three) second seal lips 32a, 32b, and 32c integrally formed with the second seal body 22t are at least two in the axial direction and the radial direction with respect to the first slinger 24. It is preferable to make it slidably contact in the direction. In the drawing, as an example, of the three second seal lips 32a, 32b, and 32c, one seal lip 32a is brought into sliding contact with the first slinger wall portion 24a in the axial direction, and the remaining two seal lips 32b. 32c are in sliding contact with the first slinger base 24b in the radial direction.

  As described above, a plurality of seal lips 28a, 28b, 28c are formed between the first seal body 20 and the second slinger 22s so as to be slidably contacted in at least two directions of the axial direction and the radial direction. By forming a plurality of seal lips 32a, 32b, 32c slidably contacting in at least two directions of the axial direction and the radial direction between the seal body 22t and the first slinger 24, the intermediate seal structure becomes the second slinger. The sliding contact force of each seal lip 28a, 28b, 28c of the first seal body 20 against 22s and the sliding contact force of each seal lip 32a, 32b, 32c of the second seal body 22t against the first slinger 24 are balanced. Maintained in position.

  The axial direction refers to a direction along the axial direction (that is, a direction parallel to the rotation axis Ax (see FIG. 6B)), whereas the radial direction refers to the radial direction. (That is, a direction perpendicular to the rotation axis Ax (see FIG. 6B)).

  As described above, according to the present embodiment, the first seal lips 28a, 28b, and 28c are provided with the second slinger while the bearing is rotating (while the stationary wheel 2 and the rotating wheel 4 are relatively rotated) or while the bearing is not rotating. The second seal lips 32a, 32b, and 32c are always in sliding contact with the first slinger 24, while being always in sliding contact with 22s. This makes it possible to prevent foreign matter (for example, water and dust) from entering the interior (space) of the bearing and to prevent leakage of the lubricant to the outside of the bearing. A pack seal 10b) can be realized.

  In this case, in the first seal body 20, a nose casket 30 is preferably formed on the first mandrel 26 (first hollow cylindrical portion 26 a) by the first seal material 28. Thereby, since the sealing state between the 1st mandrel 26 (1st hollow cylindrical part 26a) and the fixed surface 2n-2 of the stationary ring (outer ring) 2 can be improved, the inside of a bearing (space) It is possible to maintain and improve the sealing performance against the above.

  Further, according to the present embodiment, the plurality of first seal lips 28a, 28b, and 28c are slid in at least two directions, the axial direction and the radial direction, between the first seal body 20 and the second slinger 22s. In addition, the plurality of second seal lips 32a, 32b, and 32c are slidably contacted in at least two directions, the axial direction and the radial direction, between the second seal body 22t and the first slinger 24. Thus, the intermediate seal structure can be used only at the position where the sliding contact force of the first seal lips 28a, 28b, 28c and the sliding contact force of the second seal lips 32a, 32b, 32c are balanced. It can be maintained in a supported state.

  According to this, when a moment load is applied to the bearing unit, the stationary ring (outer ring) 2 and the rotating ring (inner ring) 4 are inclined relative to each other about the rotation axis Ax. When the tightening allowance of the bearing sealing device (pack seal 10b) with respect to 2 and 4 is changed and the balance state (balance) of both of the sliding contact forces described above is lost, the first and second balance amounts corresponding to the lost balance amount. Since the seal lips 28a to 28c and 32a to 32c are relatively elastically deformed, a new balanced state (balance) is formed in the above sliding contact forces.

  At this time, the intermediate seal structure is displaced (moved) to a position where a new balanced state (balance) can be achieved, and again, the plurality of first seal lips between the first seal body 20 and the second slinger 22s. The sliding contact forces of 28a, 28b, 28c and the sliding contact forces of the plurality of second seal lips 32a, 32b, 32c between the second seal body 22t and the first slinger 24 are supported at balanced positions. Maintained in a state.

  According to this, the change value (amount) of the tightening allowance of the bearing sealing device (pack seal 10b) due to the relative inclination of the outer inner rings 2 and 4 is significantly reduced compared with the existing seal (specifically Thus, the bearing sealing device (pack seal 10b) can be easily designed.

  Further, according to the present embodiment, the intermediate seal structure is interposed (inserted) between the first seal body 20 and the first slinger 24 so as to be relatively rotatable. The torque can be reduced to a certain extent. More specifically, when the outer inner rings 2 and 4 rotate relative to each other and the first slinger 24 rotates together with the rotating wheel (inner ring) 4, the second slinger 22 s rotates together with the first slinger 24. It is assumed that the motor does not rotate.

  Here, when the second slinger 22s rotates together with the first slinger 24, the plurality of first seal lips 28a, 28b, 28c slide between the first seal body 20 and the second slinger 22s. However, the plurality of second seal lips 32a, 32b, 32c do not slide between the second seal body 22t and the first slinger 24. In this case, wear of the first seal lips 28a, 28b, 28c proceeds.

  On the other hand, when the second slinger 22 s does not rotate together with the first slinger 24, that is, when only the first slinger 24 rotates, a plurality of portions between the second seal body 22 t and the first slinger 24. The second seal lips 32a, 32b, and 32c slide, and the plurality of first seal lips 28a, 28b, and 28c between the first seal body 20 and the second slinger 22s do not slide. In this case, the wear of the second seal lips 32a, 32b, and 32c proceeds.

  This is an effect obtained by adopting a structure in which the intermediate seal structure is rotatably supported at the balance position where both sliding contact forces described above are balanced. When the outer inner rings 2 and 4 are relatively rotated, The rotating state can be such that only one of the seal lips 28a, 28b, 28c or the second seal lips 32a, 32b, 32c is worn. Thereby, even if the number of seal lips is increased as compared with the existing seal structure, the rotational torque can be suppressed to the same level as that of the existing seal structure.

  Further, the intermediate seal structure is configured to be rotatably supported at the balance position where both the sliding contact forces are balanced, so that the first seal lips 28a, 28b, The rotation state in which 28c slides and the rotation state in which the second seal lips 32a, 32b, and 32c slide simultaneously cannot be specified. Thereby, the degree of wear of the seal lip can be greatly reduced as compared with the existing seal structure.

  In this case, when wear of the first seal lips 28a, 28b, 28c and / or the second seal lips 32a, 32b, 32c progresses, the first and second seal lips 28a to 28c are changed according to the degree of progress. Since 28c, 32a to 32c are relatively elastically deformed, a new balanced state (balance) is formed in the above-described sliding contact forces.

  At this time, the intermediate seal structure is displaced (moved) to a position where a new balanced state (balance) can be achieved, and again, the plurality of first seal lips between the first seal body 20 and the second slinger 22s. The sliding contact forces of 28a, 28b, 28c and the sliding contact forces of the plurality of second seal lips 32a, 32b, 32c between the second seal body 22t and the first slinger 24 are supported at balanced positions. Maintained in a state.

  According to this, the change value (amount) of the tightening allowance of the bearing sealing device (pack seal 10b) accompanying the relative inclination of the outer inner rings 2 and 4 is set to the first seal lips 28a, 28b, 28c and / or Since the amount of wear of the second seal lips 32a, 32b, and 32c can be reduced to approximately half, the bearing sealing device (pack seal 10b) can be easily designed.

  The present invention is not limited to the above-described embodiment, and the following modifications are also included in the technical scope of the present invention, and the same effects as those of the above-described embodiment can be realized.

  For example, as shown in FIG. 2A, a seal lip 28b is formed on the first seal body 20, and this is slid in the radial direction against the second slinger 22s (second slinger base 22b). A plurality of seal lips 28a, 28c are formed on the second slinger 22s, and one of the seal lips 28a is brought into sliding contact with the first seal body 20 (first hollow cylindrical portion 26a) in the radial direction; and The other seal lip 28c may be slidably contacted with the first seal body 20 (first annular folded portion 26b) in the axial direction.

  At the same time, a seal lip 32b is formed on the second seal body 22t, and the seal lip 32b is brought into sliding contact with the first slinger 24 (first slinger base 24b) in the radial direction. The seal lips 32a and 32c are molded, the one seal lip 32a is slid in the radial direction with respect to the second seal body 22t (second hollow cylindrical portion 34a), and the other seal lip 32c is The second seal body 22t (second annular folded portion 34b) may be slid in the axial direction.

  For example, as shown in FIG. 2 (b), a plurality of first seal lips 28a, 28b, 28c formed on the first seal body 20 are shaped so that the first seal lips 28a, 28b, 28c are not inverted. It may be configured. According to this configuration, the bearing sealing device (pack seal 10b) can be diverted as a wheel-side bearing sealing device. In addition, since the other structure is the same as that of the sealing device for bearings shown in FIG.1 (b), the description is abbreviate | omitted.

  For example, as shown in FIG. 3 (a), a seal lip 28b is formed on the first seal body 20, and this is slid in the radial direction against the second slinger 22s (second slinger base 22b). A plurality of seal lips 28a, 28c are formed on the second slinger 22s, and one of the seal lips 28a is brought into sliding contact with the first seal body 20 (first hollow cylindrical portion 26a) in the radial direction; and The other seal lip 28c may be slidably contacted with the first seal body 20 (first annular folded portion 26b) in the axial direction. In addition, since the other structure is the same as that of the sealing device for bearings shown in FIG.1 (b), the description is abbreviate | omitted.

  For example, as shown in FIG. 3B, a seal lip 32b is formed on the second seal body 22t, and this is slid in the radial direction against the first slinger 24 (first slinger base 24b). A plurality of seal lips 32a, 32c are formed on the first slinger 24, one of the seal lips 32a is slid in a radial direction with respect to the second seal body 22t (second hollow cylindrical portion 34a), and The other seal lip 32c may be brought into sliding contact with the second seal body 22t (second annular folded portion 34b) in the axial direction. In addition, since the other structure is the same as that of the sealing device for bearings shown in FIG.1 (b), the description is abbreviate | omitted.

  For example, as shown in FIG. 4A, in the intermediate seal structure, the second annular folded portion 34b of the second seal body 22t (core metal 34) and the second slinger wall portion 22a of the second slinger 22s. And may be configured to be used together. As a result, the bearing sealing device can be made compact in the radial direction by the amount that the second annular folded portion 34b and the second slinger wall portion 22a are combined with each other. It is possible to reduce the radial size of the bearing unit to which the sealing device is applied.

  If the grease lip 32c (see FIG. 1B) cannot be formed between the second seal body 22t and the first slinger 24, the first seal body 20 and the second seal body 20 The grease lip 28c formed between the slinger 22s and the slinger 22s may be extended and slidably brought into contact with the fitting surface 16m of the other raceway ring 4 (rotating ring component 16). In addition, since the other structure is the same as that of the sealing device for bearings shown in FIG.1 (b), the description is abbreviate | omitted.

  For example, as shown in FIG. 4B, a plurality of first seal lips 28a, 28b, and 28c formed on the first seal body 20 are shaped so that the first seal lips 28a, 28b, and 28c are not inverted. It may be configured. According to this configuration, the bearing sealing device (pack seal 10b) can be diverted as a wheel-side bearing sealing device. In addition, since the other structure is the same as that of the sealing device for bearings shown in FIG.1 (b), the description is abbreviate | omitted.

  For example, as shown in FIG. 5 (a), between the first seal body 20 and the second slinger 22s, two first types specialized for balancing in the axial direction and the radial direction are provided. Only the seal lips 28a, 28b are configured, and thereby the intermediate seal structure is maintained in a state of being supported at a position balanced with the sliding contact force of the second seal lips 32a, 32b, 32c. Good.

  According to such a configuration, the bearing sealing device can be made compact in the radial direction. As a result, the bearing unit to which the bearing sealing device is applied can be downsized in the radial direction. . In addition, since the other structure is the same as that of the sealing device for bearings shown in FIG.1 (b), the description is abbreviate | omitted.

  For example, as shown in FIG. 5B, instead of the first seal body 20, a fitting portion 36 that can be fitted to one of the race rings 2 (stationary ring (outer ring)) is integrated with the intermediate seal structure. It may be configured. As a result, the number of parts of the bearing sealing device can be reduced and the size in the radial direction can be reduced as much as the first seal body 20 is eliminated. As a result, the cost of the bearing unit to which the bearing sealing device is applied can be reduced and the size in the radial direction can be reduced. In addition, since the other structure is the same as that of the sealing device for bearings shown in FIG.1 (b), the description is abbreviate | omitted.

  In the above-described embodiments and modifications, the bearing sealing device applied to the third generation bearing unit (see FIG. 6A) is assumed, but the present invention is not limited to this, and the present invention is not limited thereto. The bearing sealing device can be applied to all types of bearing units.

  Moreover, the above-described embodiment and each modification are examples of the present invention, and the present invention is not limited to this. For example, the above-described embodiment and each modification are combined with each other according to the purpose of use and the use environment. be able to.

2 One bearing ring (stationary ring (outer ring))
4 Other race ring (rotating ring (inner ring))
20 first seal body 24 first slinger 22t second seal body 22s second slinger 28a, 28b, 28c first seal body seal lips 32a, 32b, 32c second seal body seal lip

Claims (4)

A bearing sealing device for sealing a bearing interior provided between bearing rings arranged to face each other so as to be relatively rotatable,
A first seal body that is fitted to one of the bearing rings and continuously provided along the circumferential direction so as to cover the bearing interior;
A first slinger that is fitted to the other race and is provided continuously along the circumferential direction so as to cover the inside of the bearing;
An intermediate seal structure interposed between the first seal body and the first slinger so as to be relatively rotatable, and provided continuously along the circumferential direction so as to cover the inside of the bearing;
The intermediate seal structure is configured by integrating a second slinger with which a seal lip formed on the first seal body is in sliding contact with a second seal body with a seal lip formed in sliding contact with the first slinger. A bearing sealing device, characterized in that Between the first seal body and the second slinger, there are configured a plurality of seal lips that are in sliding contact with at least two directions of the axial direction and the radial direction,
2. The bearing for a bearing according to claim 1, wherein a plurality of seal lips are formed between the second seal body and the first slinger in sliding contact with at least two directions of an axial direction and a radial direction. Sealing device. The first slinger is positioned closer to the outside of the bearing than the second seal body, and includes a first slinger wall portion having a hollow disk shape extending so as to cover the inside of the bearing, and a first slinger wall portion. A first slinger base having a hollow cylindrical shape extending toward the inside of the bearing,
The second slinger is positioned closer to the outside of the bearing than the first seal body, and includes a second slinger wall portion having a hollow disk shape extending so as to cover the inside of the bearing, and a second slinger wall portion. The bearing sealing device according to claim 2, further comprising: a second slinger base portion having a hollow cylindrical shape extending toward the inside of the bearing.   The intermediate seal structure includes a sliding contact force of the plurality of seal lips between the first seal body and the second slinger, and a sliding contact force of the plurality of seal lips between the second seal body and the first slinger. The bearing sealing device according to claim 2, wherein the bearing is maintained in a state of being supported at a balanced position.

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