JP2017009035A - Roller bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a roller bearing which can absorb a dimensional change (elongation/contraction) of a shaft which is supported by the bearing in an axial line direction, and is reducible in a dimension in the axial line direction.SOLUTION: A roller bearing 20 having an inner ring 22, an outer ring 21 and a plurality of rollers 23 whose end faces in pairs are formed at both ends in an axial line direction comprises a snap ring groove 22b formed at an end face in the axial line direction of a bearing ring of either of the inner ring and the outer ring, and a snap ring 24. The snap ring has: a radial engagement part which is engaged with the snap ring groove in a radial direction; an inhibition part 24c which abuts on and is engaged with an end face of the bearing ring in the axial line direction at the outside in the axial line direction of the roller bearing from the radial engagement part 24e, and opposes the roller end faces 23c; and a connecting part 24d which connects the radial engagement part and the inhibition part.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a roller bearing, and more particularly to a roller bearing used in general industrial machines, steel, construction machines, and the like.

  In the case of roller bearings used in general industrial machinery, steel, construction machinery, etc., when the applied load is large, to increase the load capacity of the bearing even if the outer diameter, inner diameter, and width of the bearing are the same due to restrictions on the structure around the bearing A full-roller type roller bearing is used in which the cage is eliminated and the number of rollers is increased. Cylindrical roller bearings, which are a kind of such roller bearings, guide the cylindrical rollers in the circumferential direction with an annular collar provided at the end of the inner ring or outer ring so that the bearings can be assembled and disassembled. At least one of the end portions of the inner and outer rings has no collar.

  However, the cylindrical roller (hereinafter, also simply referred to as “roller”) falls off when the raceway is removed without the collar, so that the mounting groove that continues in the circumferential direction on the peripheral surface of the end without the collar is used. And a C-shaped retaining ring is mounted in the groove (see, for example, Patent Document 1). The retaining ring prevents the cylindrical roller from moving in the axial direction of the raceway ring and prevents the cylindrical roller from falling off.

FIG. 4 is a partial sectional view showing an example of such a full-roller type roller bearing with a retaining ring.
In the roller bearing 120 with a retaining ring, a plurality of cylindrical rollers 123 are disposed so as to be able to roll in the circumferential direction between an outer ring 121 with both collars 121a and 121a and an inner ring 122 without a collar. In the vicinity of both end faces in the axial direction (width direction) of the inner ring 122 having no collar, a concave groove 122b continuous in the circumferential direction is provided, and a C-shaped retaining ring 124 is attached to the concave groove 122b.

  The C-shaped retaining ring 124 is an annular member that is partly cut in the circumferential direction so that its diameter can be expanded. It is moved inward and is fitted into the concave groove 122b by a springback.

JP 9-177770 A

  However, in the case of the above-described conventional roller bearing 120 with a retaining ring, a process for forming the concave groove 122b on the raceway surface 122a of the inner ring 122 is required. Further, the formation of the concave groove 122b inevitably increases the axial dimension of the inner ring 122. That is, the concave groove 122b that accommodates the retaining ring 124 must be formed at a position slightly inward from the both end surfaces in the width direction of the inner ring 122 by a distance d. On the other hand, the dimension Lr of the roller 123 in the axial direction (longitudinal direction) needs to be a predetermined length or more in relation to the magnitude of the burden load. And if the shafts supported by the roller bearings are the shafts at both ends of the guide roll used in, for example, continuous casting equipment, the temperature change due to contact / non-contact with the slab of the guide roll or the slab itself that contacts The guide roll expands and contracts in the longitudinal direction under the influence of the temperature change.

For this reason, it is necessary to provide a space s that can absorb the expansion / contraction amount between the roller end face 123c and the retaining ring 124. If the space s is not secured, the retaining ring 124 may be pushed in the axial direction due to the expansion and contraction of the guide roll, and may be detached from the concave groove 122b. After all, the dimension B in the axial direction of the bearing requires the following dimensions.
(Equation 1)
B ≧ Lr + 2 (s + w + d) (1)
Lr: Axial dimension of roller s: Space between roller end face and retaining ring w: Width of concave groove d: Distance between inner ring end face and concave groove

  As described above, when the groove surface is formed on the raceway surface 122a of the inner ring 122, the length substantially the same as the width of the inner ring 122 cannot be used as a full raceway surface. For this reason, when it is going to secure the axial direction dimension Lr of a roller, the axial direction dimension of an inner ring will become large inevitably. Further, although the distance d between the inner ring end face and the concave groove 122b is necessary for forming the concave groove 122b, it is a so-called dead space, and therefore the dimension B in the axial direction of the bearing is inevitably increased. Therefore, if the raceway surface of the inner ring is not subjected to groove processing and the raceway surface can be fully used, the expansion and contraction in the longitudinal direction of the guide roll can be absorbed by the space s, and the dimension B in the axial direction of the bearing can be reduced. It becomes possible to suppress. As a result, an increase in the size of the entire continuous casting facility can be avoided.

  The present invention has been made on the basis of the above-described considerations, and does not perform groove processing on the raceway surface of the bearing ring, but moves the position of the retaining ring that contacts the roller end surface to the end surface of the raceway ring. An object of the present invention is to provide a roller bearing capable of absorbing a change in dimension (elongation and contraction) in the axial direction of a shaft supported by the bearing and reducing the axial dimension of the bearing.

In order to solve the above problems, a roller bearing according to the present invention is configured as follows.
In a roller bearing having an inner ring, an outer ring, and a plurality of rollers provided between the inner ring and the outer ring and having a pair of end faces formed at both axial ends,
A retaining ring groove provided on an end surface in the axial direction of one of the inner ring and the outer ring,
A radial engagement portion that engages with the retaining ring groove in a radial direction, and abuts and engages with the end surface in the axial direction of the bearing ring on the outer side in the axial direction of the roller bearing from the radial engagement portion; A retaining ring having an opposing stop part, and a connecting part that connects the radial engagement part and the stop part;
A roller bearing characterized by comprising:

  According to the present invention, the retaining ring has a substantially L-shaped cross-section, and the restraining portion facing the roller end surface abuts and engages with either the inner ring or the outer ring axial end surface and By facing the roller end surface, the stop portion of the retaining ring does not come into contact with the roller end surface even when the axial dimension of the shaft integrated with the inner ring or outer ring with which the retaining ring is engaged (extension / shrinkage). And it becomes possible to make the dimension of the axial direction of a bearing small.

It is a schematic block diagram of the continuous casting installation to which the roller bearing which concerns on this invention was applied. FIG. 2 is a cross-sectional view of a guide roll of the continuous casting facility of FIG. 1 and a bearing device that supports the guide roll. It is explanatory drawing of the roller bearing which concerns on this invention. It is explanatory drawing of the conventional roller bearing.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 shows a continuous casting facility to which the roller bearing of the present invention is applied. In this continuous casting equipment, the molten steel in the ladle 1 is fed in the order of the tundish 2 and the mold (mold) 3, and the slab FE that has started to solidify in the mold 3 is fed between the guide rolls 4. . Immediately below the mold 3, the slab FE is cooled to promote solidification.

  FIG. 2 is a cross-sectional view showing the configuration of the guide roll 4 and the bearing device that supports the guide roll 4. In the present embodiment, the same bearing devices 10 and 10 are used, but they are reversed, and therefore only one of them will be described. In FIG. 2, the guide roll 4 includes a first cylindrical portion 4 b and a second cylindrical portion 4 b that are smaller in diameter than the rolling portion 4 a and coaxially arranged on both sides in the axial direction of the rolling portion 4 a that rolls the slab FE (see FIG. 1). The cylindrical part 4c and the third cylindrical part 4d are provided in this order from the rolling part 4a side.

  A cylindrical portion 11 a and a seal holding portion 11 b are coaxially formed inside the housing main body 11 whose lower surface is fixed to the base 5. A cylindrical roller bearing 20 is disposed in the cylindrical portion 11a. A seal 13 is disposed on the seal holding portion 11b, and its lip abuts on the outer periphery of the labyrinth ring 14 fitted to the first cylindrical portion 4b to seal it. The labyrinth ring 14 has a substantially U-shaped circumferential cross section, and forms a labyrinth seal as a non-contact seal by being combined with a correspondingly shaped housing body 11 with a minute gap. However, the seal structure is not limited to this.

  An annular member 15 is fitted and disposed on the outer periphery of the third cylindrical portion 4d of the housing body 11 so as to abut against the end surface of the second cylindrical portion 4c, and is fixed by a bolt B. The inner ring 22 of the cylindrical roller bearing 20 is sandwiched between the end surface of the first cylindrical portion 4 b and the annular member 15, and is fixed so as to rotate integrally with the guide roll 4. In some cases, a gap is slightly provided between the end faces of the annular member 15 and the inner ring 22 due to the mounting accuracy of the housing.

  A donut plate-like lid member 16 is attached to the housing body 11 using bolts B, and the outer ring 21 is fixed to the housing body 11. A seal 17 disposed in the central opening of the lid member 16 abuts on the annular member 15 and seals it. The housing body 11 and the lid member 16 constitute a housing. Although not illustrated, lubrication is often used by supplying grease, but an appropriate amount of lubricating oil including lubricating oil is pumped into the housing from the oil-air lubrication device through the piping, and the cylindrical roller 23 It is desirable to lubricate.

  FIG. 3 is an enlarged view showing the cylindrical roller bearing 20 according to the present invention. In FIG. 3, the cylindrical roller bearing 20 includes an outer ring 21 fitted to the inner periphery of the housing body 11, an inner ring 22 fitted to the second cylindrical portion 4 c of the guide roll 4, and the outer ring 21 and the inner ring 22. It comprises a plurality of cylindrical rollers 23 arranged.

  The outer ring 21 is formed integrally with flanges 21a and 21a extending radially inward at both ends in the axial direction so as to sandwich the cylindrical roller 23 therebetween.

  The inner ring 22 has an outer peripheral surface as a raceway surface 22a for the cylindrical roller 23, and an inner ring end face 22c (a raceway ring axial end face) is formed in a radial direction from both axial ends of the raceway face 22a. The inner ring end face 22c is provided with a pair of retaining ring grooves 22b for engaging with a retaining ring 24 described later. The retaining ring groove 22 b includes a radial groove 22 e extending in the radial direction of the inner ring 22 and an axial groove 22 d extending in the axial direction of the inner ring 22.

  The cylindrical roller 23 has a flat portion 23a at the center in the axial direction, a crowning portion 23b extending from the flat portion 23a in both end directions, and an end surface 23c. In the figure, the crowning portion 23b is exaggerated for easy understanding. The dimension of the cylindrical roller 23 in the axial direction (longitudinal direction) is slightly smaller than the dimension between the pair of flange portions 21 a and 21 a of the outer ring 21.

  The retaining ring 24 is preferably made of spring steel, is an ended annular member having a part cut in the circumferential direction, and has a substantially L-shaped cross section. That is, a radial engagement portion 24e that engages with the radial groove 22e of the inner ring 22, and a contact end engagement with the inner ring end surface 22c and the roller end surface 23c on the outer side in the axial direction of the roller bearing 20 from the radial engagement portion 24e. And an axial engaging portion 24d as a connecting portion that connects the radial engaging portion 24e and the stopping portion 24c. The axial engagement portion 24 d is engaged with the axial groove 22 d of the inner ring 22. The outer distance between the two restraining portions 24c and 24c is set to be substantially the same as the width dimension in the axial direction of the inner ring 22 to prevent interference with other members.

  When the retaining ring 24 is mounted on the inner ring 22, the retaining ring 24, which has been reduced in diameter from the side of the inner ring, is moved into the retaining ring groove 22b, and then the retaining ring 24 is expanded by a springback. A tapered portion 24t is formed at the distal end of the radial engagement portion 24e of the retaining ring 24. The tapered portion 24t engages with the radial groove 22e of the inner ring 22, so that the retaining ring 24 is in close contact with the inner ring 22. In this way, the restraining portion 24c of the retaining ring 24 and the inner ring end face 22c come into contact with each other with a pressing force.

  Next, the operation of this embodiment will be described.

  In the continuous casting facility shown in FIG. 1, the guide roll 4 rotates at an extremely low speed of about 2 to 3 rotations per minute in accordance with the supply of the cast FE. The bearing device 10 that supports the guide roll 4 rotatably supports the guide roll 4 with respect to the housing body 11.

  Here, when a large load is applied to the guide roll 4 from the slab FE, the guide roll bends and the inner ring 22 of the cylindrical roller bearing 20 is inclined with respect to the housing body 11. However, since the crowning portions 23b are formed at both ends in the axial direction (longitudinal direction) of the roller 23, a problem due to edge loading does not occur.

  Further, when the guide roll 4 is heated by the slab FE and thermal expansion occurs, the inner rings 22 of the left and right cylindrical roller bearings 20 in contact with the first cylindrical portion 4b are displaced in directions away from each other. At the same time, the retaining ring 24 provided on the side close to the guide roll attached to the inner ring 22 is also displaced in a direction away from each other. At this time, the roller 23 does not move because it is in contact with the outer ring flange 21a. However, a sufficient space is provided between the roller end surface 23c and the stop portion 24c of the retaining ring 24 as in the conventional example (see FIG. 4). Since s is secured, the roller end surface 23c and the retaining ring 24 do not come into contact with each other and the retaining ring 24 does not fall off from the retaining ring groove 22b. Therefore, the thermal expansion of the guide roll 4 can be released.

  On the other hand, when the guide roll 4 is cooled by heat bathing directly or when heat shrinkage occurs, the inner rings 22 of the left and right cylindrical roller bearings 20 that are in contact with the annular member 15 are brought closer to each other. Displace. At the same time, the retaining ring 24 provided on the side far from the guide roll 4 attached to the inner ring 22 is also displaced in a direction approaching each other. However, since a sufficient space s is secured between the roller end surface and the stop portion of the retaining ring 24, the roller end surface 23 c and the retaining ring 24 come into contact with each other and the retaining ring 24 comes off. There is no. Therefore, thermal contraction of the guide roll 4 can also be released.

  In FIG. 3, the conventional retaining ring 124 and the inner ring 122 are shown by a two-dot chain line for comparison. The width of the inner ring can be reduced by 2d (= d + d), and the axial dimension of the bearing is made compact.

  As described above, according to the roller bearing 20 according to the present embodiment, a sufficient space s can be ensured between the retaining ring 24 and the end surface 23c, and therefore, it is affected by the expansion / contraction of the guide roll 4 in the axial direction. In addition, the retaining ring 24 can be prevented from falling off from the inner ring 22, and the axial dimension of the roller bearing 20 can be made compact.

  It should be noted that the present invention should not be construed as being limited to the above-described embodiment, and of course can be modified or improved as appropriate. For example, the field to which roller bearings are applied is not limited to steel casting equipment, but can also be applied to paper machines and construction machines. Further, the retaining ring may be provided on either one of the inner rings, not on both end faces. In addition, both collars may be formed on the inner ring, and a retaining ring may be provided on the outer ring.

DESCRIPTION OF SYMBOLS 10 Bearing apparatus 20 Cylindrical roller bearing 21 Outer ring 21a collar 22 Inner ring 22a Raceway surface 22b Retaining ring groove 22c Inner ring end surface 23 Roller 23c Roller end surface 24 Retaining ring 24c Stopping part 24d Connection part 24e Radial engagement part

Claims (1)

In a roller bearing having an inner ring, an outer ring, and a plurality of rollers provided between the inner ring and the outer ring and having a pair of end faces formed at both axial ends,
A retaining ring groove provided on an end surface in the axial direction of one of the inner ring and the outer ring,
A radial engagement portion that engages with the retaining ring groove in a radial direction, and abuts and engages with the end surface in the axial direction of the bearing ring on the outer side in the axial direction of the roller bearing from the radial engagement portion; A retaining ring having an opposing stop part, and a connecting part that connects the radial engagement part and the stop part;
A roller bearing comprising:

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