JP5420352B2 - Rolling bearing device - Google Patents

Description

  The present invention relates to a rolling bearing device, and more particularly to an outer ring rotating type rolling bearing device.

  Conventionally, in a rolling bearing device, a contact type or non-contact type seal is used to prevent a lubricant such as grease enclosed in the bearing from leaking and to prevent water and foreign matter from entering from the outside. A mechanism is provided. For example, as a contact-type seal mechanism, a seal case is attached to the opening on both ends of the outer ring, a seal member is attached to the inside of the seal case, and the seal lip is elastically brought into contact with an oil drain or a rear lid. Things are known.

  By the way, this type of seal mechanism has a problem that a rolling bearing device used under rotation of the outer ring, particularly a bearing device provided with a tapered roller bearing, cannot sufficiently perform its intended function. That is, under the outer ring rotation, for example, the lubricant filled in the bearing easily flows to both ends of the bearing due to the centrifugal force accompanying the outer ring rotation, and the lubricant in the bearing is likely to be insufficient compared to the case of the inner ring rotation. Further, there is a concern that the lubricant may leak out due to the lubricant that has flowed out in a large amount pushed toward the sliding contact portion between the seal lip and the oil drainer. In addition, since this type of sealing mechanism is normally fixed to the outer ring that is rotationally driven, the point that centrifugal force is generated in the sealing lip and the pressing force on the inner diameter side is weakened also contributes to a decrease in sealing performance. ing.

  As a measure for improving the above-mentioned problem, for example, in Patent Document 1 below, a grease retaining ring is provided between tapered roller small-diameter side end surfaces adjacent to each other in the axial direction in a double row tapered roller bearing of an outer ring rotating type. Is disclosed. By providing the grease holding part in the center of the bearing in this way, the grease is gradually supplied from the holding part toward the raceway surface by the centrifugal force generated by the rotation of the outer ring, and the lack of grease on the raceway surface is solved. ing.

JP 2000-192972 A

  However, the tapered roller bearing disclosed in Patent Document 1 aims to eliminate the grease shortage on the raceway surface by suppressing the amount of grease (lubricant) flowing out to the outside of the bearing. It is not what I did. In the above tapered roller bearing, although the momentum of the grease flowing out to the outer diameter side is weakened, a large amount of grease still flows into the outer diameter side of the sealed space as a result. For this reason, even when a contact seal with excellent sealing performance is used, there is still a possibility that grease that cannot be held in the above space will be pressed against the sliding contact portion of the seal lip at a time to cause grease leakage.

  In view of the above circumstances, in the present specification, in the outer ring rotating type rolling bearing device, the technical problem to be solved by the present invention is to prevent the lubricant filled in the bearing from leaking out of the seal. To do.

The solution to the above problem is achieved by the rolling bearing device according to the first aspect of the present invention. That is, the bearing device includes a rotary side member including an outer ring, a fixed side member including an inner ring, a rolling bearing having a plurality of rolling elements disposed between a raceway surface of the inner ring and a raceway surface of the outer ring, and a rotary side In a rolling bearing device provided with a seal lip that is attached to a member and slidably contacts with a fixed side member and seals a space between an inner peripheral surface of the outer ring and an outer peripheral surface of the inner ring, in the space sealed by the seal lip A non-contact seal is further provided, the seal gap of the non-contact seal is arranged on the outer diameter side from the sliding contact portion between the seal lip and the fixed side member, and a gap forming member is attached to the rotation side member, and this gap is formed. It is characterized by the fact that the seal gap is formed between the member and the end face of the collar provided on the inner ring .
Moreover, the solution of the above-mentioned problem is also achieved by the rolling bearing device according to the second aspect of the present invention. That is, the bearing device includes a rotary side member including an outer ring, a fixed side member including an inner ring, a rolling bearing having a plurality of rolling elements disposed between a raceway surface of the inner ring and a raceway surface of the outer ring, and a rotary side In a rolling bearing device provided with a seal lip that is attached to a member and slidably contacts with a fixed side member and seals a space between an inner peripheral surface of the outer ring and an outer peripheral surface of the inner ring, in the space sealed by the seal lip A non-contact seal is further provided, and the seal gap of the non-contact seal is disposed on the outer diameter side of the sliding contact portion between the seal lip and the fixed side member, and the cylindrical gap forming member is formed on the rotating side member and the fixed side member. And the seal gap is formed between the cylindrical surfaces of both gap forming members.

  According to this configuration, since the non-contact seal is disposed further in front of the contact seal constituted by the seal lip when viewed from the bearing side, the lubricant can be used as compared with the case where the contact seal is used alone. Probability of preventing leakage increases. Further, by forming the seal gap of the non-contact seal on the outer diameter side from the sliding contact portion between the seal lip and the fixed side member, the lubricant is more influenced by centrifugal force and hardly flows into the seal gap. . Therefore, it is possible to avoid a situation where the lubricant is pushed toward the sliding contact portion of the contact seal at a time.

  In this case, a lubricant reservoir may be provided on the outer diameter side of the seal gap. In this way, the lubricant accumulated in the lubricant reservoir is strongly influenced by the centrifugal force and is difficult to enter the seal gap. In addition, the space on the outer diameter side of the space sealed by the contact seal is relatively smaller when the radial dimension is the same as that on the inner diameter side facing the fixed side member such as oil drainer. The space volume increases. Therefore, by providing a lubricant reservoir at the above position, a larger amount of lubricant can be retained than when a lubricant reservoir is provided, for example, on the axially inner side (side closer to the rolling element) of the seal gap.

  The seal gap may be formed by a gap forming member attached to one of the rotating side member and the fixed side member. When the gap forming member is attached to the rotation side member and a seal gap is formed between the gap forming member and the fixed side member, the gap forming member rotates integrally with the rotation side member such as the outer ring. Then, the lubricant that reaches the outer peripheral surface of the plate-like member constituting the non-contact seal or is adhered is blown to the outer diameter side by the centrifugal force accompanying the rotation of the plate-like member. Therefore, the lubricant can be made difficult to approach the seal gap of the non-contact seal, and the lubricant can be more reliably prevented from entering the sliding contact portion.

  Further, a cylindrical gap forming member may be attached to the rotation side member, a lubricant reservoir may be provided on the outer diameter side of the gap forming member, and a seal lip may be disposed on the inner diameter side of the gap forming member. By doing so, since the lubricant reservoir and the contact seal mechanism are arranged side by side in the radial direction, it is possible to secure a lubricant retention volume without expanding the axial dimension of the rolling bearing device. Alternatively, it is possible to reduce the size of the bearing device by reducing the axial dimension. If a cylindrical plate-shaped member is used, the effect of blowing off the lubricant by centrifugal force acts evenly over the entire outer peripheral surface, so a part of the outer peripheral surface of the plate-shaped member (for example, a portion on the relatively inner diameter side) ) Does not accumulate lubricant.

  Alternatively, a cylindrical gap forming member may be attached to the rotating side member and the fixed side member, respectively, and a seal gap may be formed between the cylindrical surfaces of both the gap forming members. According to this configuration, the seal gap formed between the plate-like member and the fixed side member (circle contact surface) is extended in the axial direction. Therefore, it is difficult for the lubricant to pass through the seal gap, and leakage of the lubricant from the sliding contact portion can be more reliably prevented.

  Furthermore, a gap forming member may be attached to the rotation side member, and a flange portion protruding toward the inner diameter side or the outer diameter side may be provided at one end portion close to the seal gap of the gap forming member. For example, by providing a flange portion protruding toward the inner diameter side at one end portion of the plate-like member, for example, one end portion on the side close to the seal gap, the flange portion is arranged between the seal gap and the sliding contact portion. . Therefore, this flange portion can function as a wall for stopping the flow of the lubricant, or a further seal gap can be formed between the flange portion and the fixed side member. Moreover, when the flange part which protrudes to an outer-diameter side is provided, this flange part functions as a kind of dam. Therefore, when the non-contact seal (plate member) is fixed to the rotation side member, the flange portion causes the lubricant to flow into the seal gap between the one end portion on the seal gap side of the plate member and the fixed side member. Therefore, a very high sealing effect can be obtained.

  Moreover, a collar part may be provided in an inner ring | wheel and a seal gap may be formed in an inner diameter side rather than the outer peripheral surface of a collar part. By determining the positional relationship between the flange and the seal gap in this way, it is possible to increase the space on the outer diameter side of the seal gap, in other words, the lubricant holding volume.

  Further, both the seal lip and the gap forming member constituting the contact seal and the non-contact seal may be attached to the seal case, and the seal case may be fitted and fixed to the outer ring. The gap forming member can be attached to either the rotating side member or the fixed side member.For example, if the gap forming member is attached to the rotating side member, the gap forming member is fixed to the seal case together with the seal lip constituting the contact seal, By fitting and fixing this to, for example, the outer ring, a seal device in which the contact seal and the non-contact seal are integrated can be incorporated into the rolling bearing.

  The rolling bearing according to the above description can prevent the lubricant supplied inside the bearing from leaking out of the seal and can stably supply the lubricant on the raceway surface. It can be suitably used as a tapered roller bearing that is easily affected by the above.

  As described above, according to the present invention, in the outer ring rotating type rolling bearing, it is possible to prevent the lubricant filled in the bearing from leaking out of the seal.

1 is an overall cross-sectional view of a rolling bearing device according to a first embodiment of the present invention. It is principal part sectional drawing of the rolling bearing apparatus shown in FIG. It is principal part sectional drawing of the rolling bearing apparatus which concerns on 2nd Embodiment of this invention. It is principal part sectional drawing of the rolling bearing apparatus which concerns on 3rd Embodiment of this invention. It is principal part sectional drawing of the rolling bearing apparatus which concerns on 4th Embodiment of this invention. It is principal part sectional drawing of the rolling bearing apparatus which concerns on 5th Embodiment of this invention. It is principal part sectional drawing of the rolling bearing apparatus which concerns on 6th Embodiment of this invention. It is principal part sectional drawing of the rolling bearing apparatus which concerns on 7th Embodiment of this invention. It is principal part sectional drawing of the rolling bearing apparatus which concerns on 8th Embodiment of this invention. It is principal part sectional drawing of the rolling bearing apparatus which concerns on 9th Embodiment of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 is a cross-sectional view of a main part of a rolling bearing device 1 according to a first embodiment of the present invention. The rolling bearing device 1 is used, for example, to rotate and support an axle of a railway vehicle. The rolling bearing device 1 is disposed at both ends of a so-called outer ring rotating tapered roller bearing 10 and the tapered roller bearing 10 in the axial direction. The apparatus mainly includes sealing devices 20 and 20 for sealing the space, and a front lid 30 and a rear lid 40 for axial positioning of the tapered roller bearing 10 in the inner ring 11. Among these, the tapered roller bearing 10 is provided on the inner ring 11 disposed on the outer periphery of the shaft 2, the outer ring 12, the tapered raceway surface 11 a provided on the outer periphery of the inner ring 11, and the outer periphery of the outer ring 12. Similarly, the conical raceway surface 12a, the plurality of tapered rollers 13 disposed so as to roll between the raceway surfaces 11a and 12a, and the plurality of tapered rollers 13 are held at predetermined intervals in the circumferential direction. The retainer 14 is provided. In this embodiment, the pair of inner rings 11 are disposed on the outer periphery of the shaft 2 in a state where they are in contact with each other in the axial direction. A spacer 15 is disposed between the pair of inner rings 11. The outer ring 12 is a double-row outer ring having two rows of raceway surfaces 12a and 12a on the inner periphery. Oil drainers 31 and 41 are disposed between the inner ring 11 on the shaft end side and the front cover 30 and between the rear cover 40 and the inner ring 11 on the shaft base end side. By tightening 30, the pair of inner rings 11, 11 disposed between the front lid 30 and the rear lid 40 via the oil drainers 31, 41 and the spacer 15 are positioned and fixed.

  Further, a small flange portion 11b that protrudes radially outward is formed on the small diameter side of the raceway surface 11a of the inner ring 11, and a large flange portion 11c that also protrudes radially outward on the large diameter side of the track surface 11a. Is formed. Here, the conical angle vertices of the tapered roller 13 and the raceway surface 11a of the inner ring 11 and the raceway surface 12a of the outer ring 12 coincide with each other at one point on the center line of the rolling bearing device 1 and are not shown. Can roll along the raceway surfaces 11a and 12a. The internal space of the tapered roller bearing 10 is filled with grease as a lubricant. For example, between the tapered roller 13 and the raceway surface 11 a of the inner ring 11, or between the tapered roller 13 and the raceway surface 12 a of the outer ring 12. Grease reaches the point. Hereinafter, the configuration and operation of the seal device 20 on the shaft base end side will be described in detail.

  FIG. 2 shows a cross-sectional view of the sealing device 20 disposed at one axial end of the rolling bearing (here, the axial base end side of the tapered roller bearing 10). The seal device 20 is disposed on the outer diameter side of the seal lip 22 and the seal lip 22 that is provided integrally with the seal case 21 and the inner diameter end of the seal case 21 to form a contact seal. , An elastic ring 23 that elastically biases the seal lip 22 toward the inner diameter side, and a gap forming member 25 that forms a seal gap 24 between the fixed side member.

  The seal case 21 is obtained, for example, by press forming of a steel plate. Here, the first outer cylinder portion 21a and the first outer cylinder portion 21a are fitted and fixed to the inner periphery of the large-diameter side end portion 12b of the outer ring 12. The second outer cylinder part 21b having a smaller diameter than the first outer cylinder part 21a connected through a step, and a flange part 21c protruding from the axial end of the second outer cylinder part 21b to the inner diameter side. A seal lip 22 as an elastic body is integrally formed at the inner diameter end portion of the flange portion 21c that is the inner diameter end of the seal case 21 (slightly inclined toward the bearing side in FIG. 2). The seal lip 22 is slidably contacted between the seal lip 22 and the inner peripheral surface of the oil drain 41 on the rear lid 40 facing in the radial direction under the urging force of the elastic ring 23 arranged on the outer diameter side thereof. A part is formed. As a result, the internal space of the rolling bearing filled with grease is sealed, and the entry of foreign matter from the outside is also prevented. In this embodiment, the oil drain 41 is fixed to the shaft 2 (see FIG. 1) with its axial end surface 41a in contact with the large-diameter end surface 11d of the inner ring 11.

  In this way, the internal space of the rolling bearing is sealed by the seal lip 22 (contact seal formed between the oil drain 41), and the seal lip 22 and the rolling bearing in the sealed internal space are sealed. A gap forming member 25 that forms a seal gap 24 with the inner ring 11 is further provided between the inner space 11 and the inner space 11. In this case, the seal gap 24 is formed on the outer diameter side of the sliding contact portion between the seal lip 22 and the oil drain 41. In this embodiment, the gap forming member 25 extends in the axial direction and is a space in the seal case 21 (specifically, a space between the oil drain 41 and the inner surface of the seal case 21 facing the oil drain 41 in the radial direction). ) In the radial direction, a flange portion 25b protruding outward from the axial end of the gap forming portion 25a, and a gap forming portion 25a from the outer diameter end of the flange 25b, It is comprised with the same cylindrical fitting part 25c extended in the same direction. Then, with the outer end face of the flange portion 25 b in contact with the flange portion 21 c of the seal case 21, the fitting portion 25 c located on the outermost diameter side is placed on the inner periphery of the second outer cylinder portion 21 b of the seal case 21. By fixing by fitting or the like, the gap forming member 25 is fixed to the rotation side member including the outer ring 12. In this case, the gap forming portion 25 a extends toward the axial bearing side, and forms a seal gap 24 between the axial end surface of the tip and the large-diameter end surface 11 d of the inner ring 11.

  In the rolling bearing device 1 having the above-described configuration, when the outer ring 12 rotates, the grease filled in the bearing starts to flow toward the large diameter side of the bearing due to the influence of centrifugal force accompanying the rotation. In the illustrated example, as indicated by a broken line arrow in FIG. 2, grease mainly flows out from the large diameter side of the tapered roller 13 to the outside of the bearing (outside the end surface on the large diameter side of the tapered roller 13). A part of the grease that has flowed out is held inside the outer cylindrical portions 21 a and 21 b of the seal case 21, and the other part is fixed to the inner peripheral surface of the seal case 21 and the inner periphery of the seal case 21. It flows along the inner surface of the annular gap forming member 25 from the outer side in the axial direction to the inner diameter side. At this time, as shown in FIG. 2, the seal gap 24 is further arranged in front of the seal lip 22 (inside the bearing), so that the grease leaks out as compared with the case where the seal lip 22 is used alone. Is prevented with high probability. In addition, by forming the seal gap 24 of the gap forming member 25 on the outer diameter side with respect to the sliding contact portion between the seal lip 22 and the oil drain 41, a large amount of grease is pushed toward the sliding contact portion at a time. Can be avoided.

  In this embodiment, the gap forming portion 25a constituting the gap forming member 25 is disposed on the outer diameter side of the seal lip 22 so as to cross the outer diameter side space in the axial direction. The grease from the outer diameter side space toward the inner diameter side is blocked, so that the penetration of the grease into the inner diameter side space of the seal case 21 with the gap forming portion 25a as a boundary is suppressed.

  Further, in this embodiment, since the gap forming member 25 is attached to the rotation side member, the gap forming member 25 rotates integrally with the outer ring 12, and reaches the outer peripheral surface of the gap forming portion 25a of the gap forming member 25 or The adhered grease is blown to the outer diameter side by the centrifugal force accompanying the rotation of the gap forming member 25. Therefore, it is possible to reliably prevent the grease from entering the inner diameter side space of the seal case 21 through the seal gap 24 between the gap forming portion 25a and the large diameter side end surface 11d of the inner ring 11.

  In addition, in this embodiment, the seal gap 24 between the gap forming member 25 and the fixed side member is formed between the large-diameter side end surface 11d of the inner ring 11, and thus, for example, as described above, the seal case 21 The grease that is about to flow into the inner diameter side along the inner surface of the gap forming member 25 can be reliably cut off, and the sealing effect can be further enhanced. Moreover, since the outer diameter side of the seal lip 22 which is more easily deformed than other places is filled with grease, there is no possibility that the seal lip 22 is pressed inward and the portion in sliding contact with the oil drain 41 is lifted. It can be further enhanced. Further, since the gap forming portion 25a has a smooth outer peripheral surface (cylindrical surface), as described above, the grease flows without a stagnation on the outer peripheral surface of the gap forming portion 25a from the bearing outer side toward the bearing side. Further, since the outer diameter of the gap forming portion 25a is formed to be substantially the same as the outer diameter of the large collar portion 11c of the inner ring 11, the grease can be smoothly returned to the inner ring 11 side. As a result, the lack of grease on the raceway surfaces 11a, 12a, etc. can be resolved and a good sliding state can be realized over a long period of time.

  Of course, by arranging the seal gap 24 of the gap forming member 25 on the inner diameter side, specifically, by making the outer diameter of the gap forming part 25a smaller than the outer diameter of the inner ring large collar part 11c, the sealing device It is also effective to increase the volume of grease that can be held in 20 (or the seal case 21). At this time, the volume of the outer diameter side space of the seal case 21 partitioned by the gap forming member 25 (gap forming portion 25a) in the internal space of the seal case 21 is the same as the dynamic space volume inside the rolling bearing. Alternatively, it is also effective to set the dimension of the seal case 21 or the arrangement position of the gap forming member 25 so as to be more than that. Since all of the grease supplied to the dynamic space inside the rolling bearing sealed by the seal lip 22 can be held in the grease reservoir in the seal case 21, the grease that cannot be held in the seal case 21 is pushed out and leaks out of the seal. The situation where it is put out can be avoided reliably. The “dynamic space volume” here is a volume obtained by subtracting the volumes of the tapered roller 13 and the cage 14 from the volume of the trajectory through which the rolling elements (the tapered rollers 13) and the cage 14 pass when the bearing rotates. And the space volume capable of being filled with grease around the cage 14).

  Although the first embodiment of the present invention has been described above, the scope of the present invention should not be construed as being limited to the embodiment, and the gap forming member 25 is further provided in the space sealed by the seal lip 22. And a seal gap 24 formed between the gap forming member 25 and the fixed side member is formed on the outer diameter side of the sliding contact portion between the seal lip 22 and the fixed side member. It goes without saying that it covers all the things you take.

  FIG. 3 shows a cross-sectional view of a main part of the rolling bearing device 1 according to the second embodiment of the present invention. The rolling bearing device 1 in FIG. 1 further includes a gap forming member 26 attached to the stationary member in addition to the gap forming member 25 attached to the rotating member, and thus the rolling bearing device according to the first embodiment. 1 and different. That is, in this embodiment, the gap forming member 26 extends in the axial direction so as to cover the tip of the gap forming part 25a of the gap forming member 25, and forms a radial seal gap 27 between the gap forming part 25a. It has a cylindrical gap forming part 26a and a flange part 26b protruding from the bearing side end of the gap forming part 26a toward the inner diameter side. In addition, the gap forming member 26 is integrated with the fixed-side member by sandwiching and fixing the flange portion 26b between the large-diameter side end surface 11d of the inner ring 11 and the axial end surface 41a of the oil drain 41 opposite to each other in the axial direction. Installed on. Of course, as shown in the illustrated example, an inner cylindrical portion 26c extending outward in the axial direction (in a direction away from the tapered roller 13) is further provided at the inner diameter end portion of the flange portion 26b, and the inner cylindrical portion 26c is provided as a bearing for the oil drain 41. The gap forming member 26 may be fixed by fitting to a small diameter surface 41b provided on the outer periphery of the side end.

  With such a configuration, the gap between the gap forming member 25 attached to the rotating side member and the inner ring 11 (which may be the seal gap 24) is the gap between the gap forming member 26 attached to the fixed side member. Since it is covered with the forming portion 26a, for example, grease can be reliably prevented from entering the inner diameter side space of the seal case 21 along the outer peripheral surface of the large collar portion 11c of the inner ring 11. In this embodiment, a cylindrical seal gap 27 extending in the axial direction is formed between the outer peripheral surface of the rotation-side gap forming portion 25a and the inner peripheral surface of the fixed-side gap forming portion 26a. . Accordingly, it is possible to prevent the grease from entering the space on the inner diameter side in the seal case 21 partitioned by the gap forming member 25 or the gap forming member 26, and reliably prevent leakage to the outside of the seal.

  FIG. 4 shows still another embodiment (third embodiment). A rolling bearing device 1 according to this embodiment is configured such that a rotation-side clearance forming portion 25a is bent at its bearing-side end portion toward an inner diameter side. It differs from the rolling bearing device 1 according to the second embodiment in that the flange portion 25d having the shape is integrally provided. In this embodiment as well, a cylindrical seal gap 27 is formed between the rotation side gap forming member 25 and the fixed side gap forming member 26. According to the above configuration, even if grease passes through the seal gap 27 and enters the inner diameter side space of the gap forming member 25, the grease flows into the sliding contact portion between the seal lip 22 and the oil drain 41. Is blocked by the flange portion 25d. For this reason, the leakage of grease to the outside of the seal is more reliably prevented.

  Alternatively, as shown in FIG. 5, it is also possible to integrally provide a flange portion 25e that protrudes to the outer diameter side of the rotation side gap forming portion 25a. In the rolling bearing device 1 according to this embodiment (fourth embodiment), a flange portion 25e in which the bearing-side end portion of the gap-forming portion 25a extending in the axial direction is bent toward the outer diameter side in the rotation-side clearance forming member 25. Is different from the rolling bearing device 1 according to the second and third embodiments. According to the above configuration, since the radial gap between the gap forming portion 25a and the gap forming portion 26a is further narrowed at the back side thereof, the radial seal gap 27 is formed. (Sealing effect) can be further enhanced. Of course, the present invention is not limited to this example, and the seal gap 27 can take various forms. For example, one or a plurality of annular oil grooves are provided on at least one of the outer peripheral surface of the rotation-side clearance forming portion 25a and the inner peripheral surface of the fixed-side clearance forming portion 26a, and the radial seal clearance 27 is an oil groove seal. It is also possible to function as. Alternatively, the outer peripheral surface of the rotation-side clearance forming portion 25a and the inner peripheral surface of the fixed-side clearance forming portion 26a are formed into a concave-convex shape, and a minute clearance is provided between these concave-convex surfaces, whereby the seal clearance 27 is formed. It is also possible to function as a labyrinth seal.

  FIG. 6: has shown principal part sectional drawing of the rolling bearing apparatus 1 which concerns on 5th Embodiment. This rolling bearing device 1 is the above-mentioned in that the gap forming member 26 on the fixed side is fitted and fixed to the outer periphery of the large collar portion 11c of the inner ring 11 instead of being sandwiched and fixed between the inner ring 11 and the oil drain 41. This is different from the rolling bearing device 1 according to the second to fourth embodiments. Specifically, the gap forming member 26 on the fixed side is provided integrally with the gap forming portion 26a disposed on the outer diameter side of the clearance forming portion 25a on the rotating side and the bearing side end of the gap forming portion 26a. And a fitting portion 26 d that can be fitted to the outer peripheral surface of the large collar portion 11 c of the inner ring 11. In FIG. 6, the fitting diameter with the large collar part 11c (the outer diameter of the large collar part 11c) and the outer diameter of the gap forming part 26a are designed to be the same. For the purpose of increasing the holding volume of the grease on the diameter side, it is possible to make the outer diameter of the clearance forming portion 26a on the fixed side smaller than the outer diameter of the large collar portion 11c. According to this configuration, the gap forming member 26 on the fixed side can be disposed at a predetermined position of the seal case 21 without changing the dimensions of the inner ring 11 or the oil drain 41.

  FIG. 7: has shown principal part sectional drawing of the rolling bearing apparatus 1 which concerns on 6th Embodiment. This rolling bearing device 1 is the same as the first to fifth embodiments in that a part of the bearing side of the rotation side clearance forming portion 25a is inclined to the outer diameter side (provided with an inclined portion 25f). This is different from the rolling bearing device 1. This configuration is based on the assumption that the grease flows in the direction indicated by the broken line arrow in FIG. 7 when the outer ring rotates. That is, in the rolling bearing device 1 (tapered roller bearing) shown in the figure, the grease filled in the bearing moves to the bearing outer diameter side due to the influence of the centrifugal force accompanying the rotation of the outer ring. Then, the grease that has been pushed to the outer diameter side due to the centrifugal force travels along the inner peripheral surface of the seal case 21 and the inner peripheral surface of the gap forming member 25, and is located on the outermost side in the seal case 21 (in this figure). It reaches the outer peripheral surface of the gap forming portion 25a along the inner end surface. In this way, when the grease flows in the seal case 21, the outer peripheral surface of the inclined portion 25f is tapered toward the bearing side by inclining the partial shaft end side of the gap forming portion 25a to the outer diameter side. It becomes the shape expanded in the shape. Therefore, the grease flowing on the outer peripheral surface of the inclined portion can be guided into the bearing, and the grease can be circulated between the seal case 21 and the bearing. In this embodiment, the flange portion 25e that protrudes toward the outer diameter provided at the bearing side end of the gap forming portion 25a functions as a weir against the grease that flows along the outer peripheral surface of the inclined portion.

  Of course, the configuration for promoting the flow circulation is not limited to the above. For example, at least the outer peripheral surface of the gap forming portion 25a is formed such that the gap forming portion 25a is inclined over the entire surface. A constant circulation action can be obtained by making the shape expand diameter continuously or stepwise as it approaches.

  FIG. 8 is a cross-sectional view of a main part of the rolling bearing device 1 according to the seventh embodiment. In the rolling bearing device 1, a flange member 28 separate from the gap forming portion 25a is fixed to the inner periphery of the fixed gap forming portion 25a, and the inner ring 11 facing the flange member 28 in the axial direction is fixed. This is different from the rolling bearing device 1 according to the first to sixth embodiments in that an axial seal gap 24 is formed between the large-diameter end face 11d. Specifically, the flange member 28 includes a cylindrical portion 28a and a flange portion 28b protruding from the one end of the cylindrical portion 28a toward the inner diameter side, and the cylindrical portion 28a is fitted and fixed to the inner periphery of the gap forming portion 25a. In addition, by appropriately adjusting the axial position, the axial distance between the flange member 28 and the inner ring 11 is set appropriately, and a disc-shaped seal gap 24 extending in the radial direction is formed between the two. Is done.

  Of course, the above configuration can also be employed when the gap forming member 26 is disposed on the fixed side in addition to the rotating side. FIG. 9 shows an example, and the rolling bearing device 1 according to this embodiment includes a seal clearance extending in the axial direction between a fixed-side clearance forming member 26 sandwiched and fixed between the inner ring 11 and the oil drain 41. 24 is formed. According to this configuration, the double seal gaps 24 and 27 extending in the radial direction and the axial direction can be formed between the rotation-side gap forming member 25 and the fixed-side gap forming member 26. Thereby, it is possible to more reliably prevent the grease from entering the inner diameter side of the gap forming member 25 (the space between the seal gap 24 and the sliding contact portion of the seal lip 22).

  Alternatively, as in the embodiment shown in FIG. 10 (the ninth embodiment), the flange portion 25d is formed by bending the end portion on the inner ring 11 side of the gap forming portion 25a of the gap forming member 25, and the flange portion 25d and the inner ring 11 are formed. A sealing gap 24 may be formed between the large-diameter end face 11d. This also can reliably prevent the grease from entering the inner diameter side.

  Further, in the above description, the gap forming portion 25a is illustrated as having a cylindrical shape and at least one that partitions the inside of the seal case 21 in the axial direction, but is not limited thereto. The seal case 21 is disposed on the sliding contact portion between the seal lip 22 and the oil drain 41, preferably on the outer diameter side of the seal lip 22, and between the inner ring 11 and the seal gap 24 ( The shape is arbitrary as long as it can be formed (regardless of the axial direction and the radial direction).

  In the above description, the case where the gap forming member 25 is attached to the rotating side, or the case where the gap forming member 25 is attached to the rotating side and the gap forming member 26 is attached to the fixed side is exemplified. It is also possible to adopt a configuration in which the gap forming member 26 is only attached. In this case, as the gap forming member 26 on the fixed side, for example, a cylindrical gap forming portion 26 a in FIG. 3 extends in a direction away from the inside of the bearing, and between the axial end surface and the flange portion 21 c of the seal case 21. It is conceivable to form an axial seal gap 24 at the same time.

  Further, in the above description, the metal seal case 21 and the seal lip 22 which is an elastic body made of resin are integrally formed at the inner diameter side end portion of the seal case 21, and the seal lip 22 is opposed in the axial direction. Although the case where the contact seal is formed by sliding on the outer peripheral surface of the oil drain 41 to be illustrated is illustrated, of course, it is not limited thereto. For example, a seal lip made of an elastic body having a Z-shaped cross section made of resin or the like is slidably contacted with the oil drain 41, and a space containing the seal lip is filled with grease or the like. The present invention can be applied to any contact-type seal that forms a seal by elastically sliding against an opposing member, such as a so-called V-ring having a seal lip made of an elastic body that slides in the thrust direction.

  In the above description, grease having a relatively high viscosity is exemplified as the lubricant. However, the present invention is not limited to this, and the present invention can be applied to other lubricants such as lubricating oil. Is possible.

  Moreover, although the above description demonstrated the case where this invention was applied to the rolling bearing apparatus 1 provided with the tapered roller bearing, the form of a tapered roller bearing is not ask | required in particular. That is, the present invention can be applied not only to the illustrated double row (2 rows, 4 rows) but also to a single row tapered roller bearing. Of course, the present invention can be applied not only to the tapered roller bearing but also to other types of roller bearings such as a cylindrical roller bearing and a spherical roller bearing. Furthermore, the present invention can be applied to all rolling bearings such as ball bearings using balls as rolling elements. In addition, it goes without saying that the rolling bearing according to the present invention can be applied to applications (general industrial machine applications, railway vehicle applications) corresponding to the various types of rolling bearings described above.

DESCRIPTION OF SYMBOLS 1 Rolling bearing apparatus 2 Shaft 10 Tapered roller bearing 11 Inner ring 11b Large diameter side end surface 11c Large collar part 12 Outer ring 12b Large diameter side end part 13 Tapered roller 14 Cage 20 Sealing device 21 Seal case 22 Seal lip 23 Elastic rings 31, 41 Oil drainer 24, 27 Seal gap 25, 26 Clearance forming member 25a, 26a Clearance forming part 25b, 26b Flange part 25c Fitting part 25d, 5e Flange part 28 Flange member

Claims (8)

A rotating side member including an outer ring, a fixed side member including an inner ring, a rolling bearing having a plurality of rolling elements disposed between a raceway surface of the inner ring and a raceway surface of the outer ring, and a fixed side attached to the rotary side member In a rolling bearing device comprising a seal lip that is in sliding contact with a member and seals a space between the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring,
A non-contact seal is further provided in the space sealed by the seal lip, and the seal gap of the non-contact seal is disposed on the outer diameter side of the sliding contact portion between the seal lip and the fixed side member , and the rotary side member is provided. A rolling bearing device in which a gap forming member is attached, and the seal gap is formed between the gap forming member and an end face of a flange provided on the inner ring .   The rolling bearing device according to claim 1, wherein a lubricant reservoir is provided on an outer diameter side of the seal gap.   2. The rolling bearing device according to claim 1, wherein a cylindrical gap forming member is attached to the rotation side member, a lubricant reservoir is provided on the outer diameter side of the gap forming member, and a seal lip is disposed on the inner diameter side of the gap forming member. . A rotating side member including an outer ring, a fixed side member including an inner ring, a rolling bearing having a plurality of rolling elements disposed between a raceway surface of the inner ring and a raceway surface of the outer ring, and a fixed side attached to the rotary side member In a rolling bearing device comprising a seal lip that is in sliding contact with a member and seals a space between the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring,
A non-contact seal is further provided in the space sealed by the seal lip, and the seal gap of the non-contact seal is disposed on the outer diameter side of the sliding contact portion between the seal lip and the fixed side member,
A rolling bearing device, wherein a cylindrical gap forming member is attached to each of the rotating side member and the fixed side member, and the seal gap is formed between the cylindrical surfaces of both of the gap forming members. At one end adjacent to the sealing gap to come between formation members, a rolling bearing device according to claim 1 provided with a flange portion protruding radially inwardly or radially outer side. A flange portion provided on the inner ring, the rolling bearing device according to any one of claims 1 to 5 formed the sealing gap on the inner diameter side than the outer peripheral surface of the flange portion. The rolling bearing device according to claim 1 , wherein the seal lip and the gap forming member are attached to a seal case, and the seal case is fitted and fixed to the outer ring. The rolling bearing device according to any one of claims 1 to 7 , wherein the rolling element is a tapered roller.

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