JP2017223286A - Full roller type cylindrical roller bearing, seal seat part and sealing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a full roller type cylindrical roller bearing capable of reducing a use amount of grease, and allowing relative movement of an inner ring and an outer ring in an axial direction while securing handleability of a bearing and assemblability to a shaft, and also provide a seal seat part and a sealing device.SOLUTION: A full roller type cylindrical roller bearing 20 includes: a seal seat part 30 provided separately from a flange part 22 of an outer ring 23, and projecting axially outward with respect to an axial end surface 23a of the outer ring 23; and a seal member 40 having a core grid 41 attached to an outer peripheral surface of the inner ring 25, and an elastic body 45 provided to a radial outside of the core grid 41 and having a tip part 46 slide-contacting with an inner peripheral surface of the seal seat part 30.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a full-roller type cylindrical roller bearing, a seal seat, and a sealing device, and more particularly, a full-roller type cylinder using grease lubrication that is applied to a guide roll for continuous casting, a table roll, a conveyor, and the like. The present invention relates to a roller bearing, a seal seat, and a sealing device.

  For roller bearings used in general industrial machinery, steel, construction machinery, etc., if the applied load is large, the load capacity of the bearing is reduced even if the outer diameter, inner diameter, and width of the bearing are the same due to structural constraints around the bearing. A full roller type roller bearing is used in which the number of rollers is increased by eliminating the cage so that a large number can be obtained.

  Cylindrical roller bearings, which are one type 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. At least one end of the both ends of the ring is made free of collars.

  However, in this case, if the raceway is removed, the cylindrical roller falls off. Therefore, a circumferentially continuous attachment groove is provided on the peripheral surface of the end portion of the raceway that is not provided with a brim, and the circumference of the attachment groove is provided. A C-shaped retaining ring in which a part of the direction is cut and a gap is provided between both ends in the circumferential direction is mounted (see, for example, Patent Documents 1 and 2). In addition to the C-shaped retaining ring, there are also those that are fitted with an annular retaining ring such as a retaining ring to prevent the cylindrical roller from falling off (see, for example, Patent Document 3).

  Also, in cylindrical roller bearings with cages, the seal body mounted on the inner peripheral surface of the outer ring is provided with a peripheral edge protruding in the axial direction, and seals are provided at two locations in the axial direction to improve sealing performance. Is known (see, for example, Patent Document 4).

JP 09-177770 A Japanese Patent Laid-Open No. 2004-218776 Japanese Utility Model Publication No. 05-047538 Japanese Utility Model Publication No. 58-092525

  By the way, as described above, as a function required for the full-roller cylindrical roller bearing used on the free side of the guide roll or the like, in order to improve the handleability of the bearing and the assembly to the shaft, A retaining ring that restricts axial movement is required. Also, since the periphery of such a bearing is used in a harsh environment covered with water, water vapor, and scale, a sealing device should be used for the bearing to prevent water, dust, etc. from entering the bearing. Is desired.

  For this reason, as a full complement cylindrical roller bearing provided with both a retaining ring and a sealing device, the configuration shown in FIG. 13A and FIG. 14A can be considered. For example, in the full complement cylindrical roller bearing 100 shown in FIG. 13A, the retaining rings 110, 110 are attached to the inner ring 101, and the seal members 120, 120 are attached to the outer ring 102. The lip portions 121 and 121 are in sliding contact with the outer peripheral surface of the inner ring 101. In addition, in the full complement cylindrical roller bearing 100a shown in FIG. 14 (a), the retaining rings 110, 110 are attached to the inner ring 101, and the seal members 120, 120 are attached to the inner ring 101 inside the retaining rings 110, 110 in the axial direction. The lip portions 121 and 121 are in sliding contact with the inner peripheral surface of the outer ring 102.

Further, in a structure having such a retaining ring and a sealing device, it is further required to secure as large an amount of movement in the axial direction as possible due to the extension of the inner ring. However, as shown in FIGS. 13 (b) and 14 (b), any of the full-roller cylindrical roller bearings 100 and 100a interferes with the retaining ring 110 or the cylindrical roller 103 and the seal member 120, or has a sealing performance. Because of the maintenance, it is difficult to secure large amounts of movement X ₁ and X ₂ .

  Further, in the cylindrical roller bearing described in Patent Document 4, the axial movement of the race is not taken into consideration. In particular, in the seal structure shown in FIG. 5 of Patent Document 4, due to the followability of the two lips and the side lip, the inner ring can be slightly displaced in the axial direction but cannot be displaced greatly in the axial direction.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to reduce the amount of grease used, and to secure the shaft handling of the inner ring and the outer ring while ensuring the handling property of the bearing and the assembling property to the shaft. An object of the present invention is to provide a full-roller cylindrical roller bearing, a seal seat, and a sealing device that allow relative movement in a direction.

The above object of the present invention can be achieved by the following constitution.
(1) a pair of races comprising an outer ring and an inner ring;
A plurality of cylindrical rollers disposed between both raceway surfaces of the pair of raceways;
With
Of the pair of race rings, one of the race rings has a flange portion extending radially in the axial direction outside of the raceway surface, grease is sealed in a bearing space, and the pair of race rings The bearing ring of this is a full-roller cylindrical roller bearing capable of relative displacement in the axial direction,
A seal seat provided integrally with or separately from the collar,
A seal member that is attached to the other race ring and includes a tip portion that is in sliding contact with or in close proximity to the peripheral surface of the seal seat;
A full-roller type cylindrical roller bearing further comprising:
(2) The full-roller cylindrical roller bearing according to (1), wherein the seal seat protrudes outward in the axial direction from the axial end surface of the one raceway ring.
(3) The one raceway ring has a pair of flanges extending in the radial direction on the outer side in the axial direction of the raceway surface,
The pair of collars are provided with a pair of seal seats provided integrally or separately, and
The full-roller type cylindrical roller bearing according to (1) or (2), wherein the pair of seal members are provided such that the tip portions are in sliding contact with or in close proximity to the peripheral surfaces of the pair of seal seat portions, respectively. .
(4) The peripheral surfaces of the pair of seal seats have an axial length in which the tip ends are always in sliding contact or close to each other when the pair of race rings are relatively displaced in the axial direction. The full roller type cylindrical roller bearing according to (3).
(5) The full-roller type cylindrical roller bearing according to any one of (1) to (4), wherein the seal seat portion has a grease reservoir recessed in an axially inner side surface thereof.
(6) The seal member is a cored bar attached to the peripheral surface of the other raceway ring, and the tip that is provided on the flange part of the cored bar and is in sliding contact with or close to the peripheral surface of the seal seat part A full roller cylindrical roller bearing according to any one of (1) to (5), comprising an elastic body having a portion.
(7) The metal core of the seal member includes a cylindrical portion that fits to the peripheral surface of the other raceway ring, and the flange portion that extends in a radial direction from an axial end of the cylindrical portion. The full roller cylindrical roller bearing according to (6), which is an L-shaped annular member.
(8) Of the pair of bearing rings of the cylindrical roller bearing, a main body having an attachment surface that can be attached to the flange of one of the bearing rings;
It is formed in an annular shape having a protruding portion that protrudes outward in the axial direction from the axial side surface of the main body portion on the other raceway side in the radial direction from the main body portion. Seal seat.
(9) The seal seat according to (8),
A cored bar that can be attached to the peripheral surface of the other bearing ring of the cylindrical roller bearing, and a tip part that is provided on the flange part of the cored bar and that slidably contacts or closely faces the peripheral surface of the seal seat part. A sealing member comprising an elastic body,
A sealing device comprising:

  According to the full complement cylindrical roller bearing of the present invention, a seal seat provided integrally with or separately from the collar portion of one of the race rings, and attached to the other race ring and in sliding contact with the peripheral surface of the seal seat portion. Or a sealing member provided with the front-end | tip part which adjoins and opposes. As a result, the bearing space can be sealed to reduce the amount of grease used, and in the axial direction of the inner ring and the outer ring, which are a pair of race rings, while ensuring the handleability of the bearing and the ease of assembly to the shaft. Relative movement can be allowed.

  Further, according to the seal seat portion and the sealing device of the present invention, the seal seat portion can be attached to the flange portion of one of the race rings and protrudes outward in the axial direction from the axial end surface of the one race ring. Therefore, in the cylindrical roller bearing that allows the relative movement in the axial direction of the inner ring and the outer ring, which are a pair of race rings, the sealability of the bearing space can be improved.

It is a perspective view which shows the outline of the continuous casting apparatus using the full roller type cylindrical roller bearing based on 1st Embodiment of this invention. It is sectional drawing of the bearing apparatus with which the full roller type cylindrical roller bearing of 1st Embodiment was attached to the edge part of a roll. (A) is sectional drawing which shows the full-roller type cylindrical roller bearing of FIG. 2, (b) is sectional drawing which shows the full-roller type cylindrical roller bearing of the state which the outer ring and the inner ring displaced relatively in the axial direction. . It is sectional drawing which shows the full complement type cylindrical roller bearing of 2nd Embodiment. It is sectional drawing which shows the full complement type cylindrical roller bearing of 3rd Embodiment. It is sectional drawing which shows the full complement type cylindrical roller bearing of 4th Embodiment. It is sectional drawing which shows the full complement type cylindrical roller bearing of 5th Embodiment. It is sectional drawing which shows the full complement type cylindrical roller bearing of 6th Embodiment. It is sectional drawing which shows the full complement type cylindrical roller bearing of 7th Embodiment. It is sectional drawing which shows the full complement type | mold cylindrical roller bearing which concerns on the modification of 7th Embodiment. It is sectional drawing which shows the full complement type cylindrical roller bearing of 8th Embodiment. (A)-(i) is principal part sectional drawing which shows the modification of an elastic body. (A) is sectional drawing which shows the full roller cylindrical roller bearing as a reference example, (b) is sectional drawing which shows the full roller cylindrical roller bearing to which the inner ring and the outer ring moved relatively. (A) is sectional drawing which shows the full roller cylindrical roller bearing as another reference example, (b) is sectional drawing which shows the full roller cylindrical roller bearing to which the inner ring and the outer ring moved relatively.

  Hereinafter, a full-roller type cylindrical roller bearing, a seal seat, and a sealing device according to each embodiment of the present invention will be described in detail with reference to the drawings.

(First embodiment)
First, a continuous casting facility to which the full-roller cylindrical roller bearing 20 of the present embodiment (hereinafter simply referred to as “cylindrical roller bearing 20”) is applied will be described.
In this continuous casting facility, as shown in FIG. 1, molten steel in a ladle 1 is fed in the order of a tundish 2 and a mold (mold) 3, and a cast FE that has started to solidify in the mold 3 is a guide roll. It is sent between four. Immediately below the mold 3, the slab FE is cooled to promote solidification.

  As shown in FIG. 2, the guide roll 4 has axial end portions 4b having a smaller diameter than the rolling portion 4a on both sides in the axial direction of the rolling portion 4a (see FIG. 1) for rolling the slab FE. The guide roll 4 is rotatable with respect to the housing 5 by supporting the axial end 4 b of the guide roll 4 by the cylindrical roller bearing 20.

Referring also to FIG. 3, the full-roller cylindrical roller bearing 20 includes an outer ring raceway surface 21 formed on the inner peripheral surface and a pair of axially outer sides extending outward in the axial direction of the outer ring raceway surface 21. An outer ring 23 having flanges 22, 22, an inner ring 25 having an inner ring raceway surface 24 formed on the outer peripheral surface, and a full-roller type having no cage between the outer ring raceway surface 21 and the inner ring raceway surface 24. And a plurality of cylindrical rollers 26, and grease is sealed in the bearing space.
In the present embodiment, the outer ring 23 constitutes one raceway of the present invention, and the inner race 25 constitutes the other raceway.

The outer ring 23 is in contact with a step portion 5 a formed on the inner peripheral surface of the housing 5, and is positioned in the axial direction by fastening the lid member 7 with a bolt via the outer ring spacer 6. Further, the inner ring 25 is brought into contact with the step 4c of the axial end 4b of the guide roll 4, and is positioned in the axial direction by mounting the retaining ring 8 in the groove 4d formed in the axial end 4b. Yes.
In addition, on the axially outer side of the cylindrical roller bearing 20 (on the right side of the cylindrical roller bearing 20 in FIG. 2), between the housing 5 and the ring member 9 disposed around the axial end portion 4 b of the guide roll 4. Two sealing devices 10, 10 are provided.

  The full-roller cylindrical roller bearing 20 is provided separately from the flanges 22 and 22 of the outer ring 23, and has a pair of seal seats 30 that protrude outward in the axial direction from the axial end surface 23 a of the outer ring 23. A cored bar 41 attached to the outer peripheral surface of the inner ring 25, and an elastic body 45 provided on the radially outer side of the cored bar 41 and having a distal end portion 46 that is in sliding contact with the inner peripheral surface of the seal seat 30. And a pair of seal members 40. That is, the cylindrical roller bearing 20 includes a pair of sealing devices 50 each having a seal seat portion 30 and a seal member 40 on both sides in the axial direction.

  The seal seat portion 30 includes a main body portion 32 having a mounting surface 31 fitted and attached to the inner peripheral surface of the flange portion 22 of the outer ring 23, and a radially inner side of the main body portion 32. And a projecting portion 33 projecting outward in the axial direction from the side surface 32a. A convex portion 34 is formed on the outer peripheral surface of the main body portion 32, and is positioned in the axial direction by fitting into a groove portion 23 b formed on the inner peripheral surface of the flange portion 22. Further, the seal seat portion 30 has a grease reservoir portion 35 that is recessed on the inner side surface in the axial direction, and opens to the end surface in the axial direction of the cylindrical roller 26.

The axially outer side surface 32a of the main body 32 is formed flush with the axial end surface 23a of the outer ring, and the axially inner side surface 32b of the main body 32 is flush with the axially inner side surface 22a of the flange 22 of the outer ring. Formed.
In the present embodiment, the seal seat portion 30 is formed of a metal material, but the material is not limited as long as the inner peripheral surface functions as a sliding contact surface that contacts the sealing member 40. For example, a material made of nitrile, nitrile hydroxide, fluorine, Teflon (registered trademark), or acrylic can be used.

  The metal core 41 of the seal member 40 includes a cylindrical portion 42 that fits into a fitting groove 25a formed on the outer peripheral surface of the inner ring 25, and a flange portion 43 that extends radially outward from the axial end of the cylindrical portion 42. Is an annular member having a substantially L-shaped cross section. The elastic body 45 is provided so as to cover the outer diameter portion of the flange portion 43.

  The pair of seal members 40 are attached to the inner ring 25 with a clearance X between the axial end surface of the cylindrical rollers 26 so that the outer ring 23 and the inner ring 25 can be relatively displaced in the axial direction. . The pair of seal members 40 can act as a retaining ring for restricting the inner ring 25 in the axial direction with respect to the cylindrical roller 26 during assembly of the bearing and the like. Assemblability can be improved.

  Moreover, it is preferable that the inner peripheral surface of the seal seat portion 30 has an axial length in which the distal end portion 46 of the elastic body 45 is always in sliding contact when the outer ring 23 and the inner ring 25 are relatively displaced in the axial direction. Therefore, for example, as shown in FIG. 3B, the inner ring 25 is axially moved until the seal member 40 on one side (the right side) contacts the axial end surface of the cylindrical roller 26 due to the extension of the shaft (guide roll 4). Even if it moves to the left, the tip 46 of the elastic body 45 of the other (left) seal member 40 can maintain sliding contact with the inner peripheral surface of the seal seat 30.

For this reason, the protrusion amount B of the protruding portion 33 of the seal seat portion 30 shown in FIG. 3A is such that the distal end portion 46 of the elastic body 45 always slides when the outer ring 23 and the inner ring 25 are relatively displaced in the axial direction. It is preferable to set the axial length so as to be in contact with each other. However, the protruding amount B of the protruding portion 33 needs to be designed so as not to interfere with components around the cylindrical roller bearing 20. Accordingly, the protrusion amount B of the protrusion 33 and the gap X between the seal member 40 and the axial end surface of the cylindrical roller 26 are designed to be as large as possible in consideration of the layout around the cylindrical roller bearing 20. It is preferable.
Further, when the relative movement amount of the inner ring 25 in the axial direction with respect to the outer ring 23 is smaller than the gap X, the protrusion amount B of the protruding portion 33 may be designed according to the relative movement amount.

  As described above, according to the full complement cylindrical roller bearing 20 of the present embodiment, the pair of seal seats 30 provided separately from the pair of flanges 22 of the outer ring 23 and the outer peripheral surface of the inner ring 25 are provided. A pair of sealing members 40 each provided with a cored bar 41 to be attached and an elastic body 45 provided on the radially outer side of the cored bar 41 and having a distal end portion 46 slidably contacting the inner peripheral surface of the seal seat 30; Have. Thereby, the bearing space of the full-roller cylindrical roller bearing 20 can be sealed, and the amount of grease used can be reduced. Also suitable for supporting the end on the free side by allowing relative movement in the axial direction of the inner ring and outer ring due to the elongation of the inner ring while ensuring the handleability of the bearing and the assembly to the shaft. can do.

  Further, since the pair of seal seats 30 includes the protruding portion 33 that protrudes outward in the axial direction from the axial end surface 23a of the outer ring 23, when the width dimension of the inner ring 25 is restricted, the sealing member 40 is Sliding in the axial direction exceeding the width dimension of the inner ring 25 is possible, and the degree of freedom in designing the bearing can be increased.

  Further, the inner circumferential surface of the seal seat portion 30 has an axial length in which the distal end portion 46 of the elastic body 45 is always in sliding contact with the inner ring 25 when the outer ring 23 and the inner ring 25 are relatively displaced in the axial direction. Even when the relative movement of the outer ring 23 is allowed, the sealing performance can be maintained.

  Furthermore, since the seal seat portion 30 has the grease reservoir portion 35 recessed on the inner side surface in the axial direction, more grease can be enclosed in the bearing space.

  The metal core 41 of the seal member 40 includes a cylindrical portion 42 that fits to the outer peripheral surface of the inner ring 25, and a flange portion 43 that extends radially outward from the axial end of the cylindrical portion 42. Since it is an L-shaped annular member, even if relative movement between the inner ring 25 and the outer ring 23 is allowed, sealing performance can be ensured between the seal seat 30 and the seal member 40.

(Second Embodiment)
Next, a full-roller cylindrical roller bearing 20a according to a second embodiment will be described with reference to FIG. The full-roller cylindrical roller bearing 20a of the present embodiment is different from that of the first embodiment in the configuration of the core member 41a of the seal seat 30a and the seal member 40a.

  The seal seat portion 30a of this embodiment is inserted so as to abut on a stepped portion 22b formed on the inner peripheral surface of the flange portion 22, and is attached to a mounting groove 22c formed on the inner peripheral surface of the flange portion 22. By inserting 36, it is positioned and fixed in the axial direction. The axially outer side surface 32a of the main body 32 of the seal seat 30a is located on the inner side in the axial direction with respect to the axial end surface 23a of the outer ring 23, while the protruding portion 33 has a protrusion amount B and the axial end surface 23a of the outer ring 23. It is located outside in the axial direction.

  In the present embodiment, the axially inward protruding portion 38 extending inward in the axial direction is formed on the seal seat 30a so that the axially inner side surface 32b of the seal seat 30a is also closely opposed to the end surface of the cylindrical roller 26. The Thereby, even if the inner ring 25 and the outer ring 23 move relative to each other, the seal member 40a is in sliding contact with the inner peripheral surface of the seal seat portion 30a.

  Furthermore, in this embodiment, the grease reservoir 35 includes the radially inner peripheral surface of the flange portion 22, the radially outer peripheral surface of the axially inwardly protruding portion 38, and the axially inner surface of the main body portion 32 therebetween. It is defined by.

  In the present embodiment configured as described above, the ease of disassembly and assembly of the seal seat 30a can be improved, so that the maintainability can be improved.

Further, in the seal member 40a of the present embodiment, a convex portion 42a that fits into the concave portion 25b formed in the fitting groove 25a is formed at the axial end of the cylindrical portion 42 of the cored bar 41a. It is possible to more reliably prevent the member 40a from falling off.
Other configurations and operations are the same as those in the first embodiment.

(Third embodiment)
Next, a full roller type cylindrical roller bearing 20b according to a third embodiment will be described with reference to FIG. Note that the full-roller cylindrical roller bearing 20b of this embodiment is different from that of the second embodiment in the configuration of the seal seat portion 30b.

  The seal seat portion 30b of the present embodiment has a flange-like body portion 32 abutted against a notch portion 23c formed on the flange portion 22 from the axial end surface 23a of the outer ring 23, and is fixed by a screw 37. Yes. In this case, the axially outer surface 32a of the main body 32 and the axial end surface 23a of the outer ring 23 are substantially flush with each other.

  Further, the protruding portion 33 is located at the outer side in the axial direction with respect to the axial end surface 23 a of the outer ring 23 with the protruding amount B. Further, in the seal seat portion 30b, an axially inward protruding portion 38 extending inward in the axial direction is formed so that the axially inner side surface 32b thereof is in close proximity to the end surface of the cylindrical roller 26. Thereby, even if the inner ring 25 and the outer ring 23 move relative to each other, the seal member 40a is in sliding contact with the inner peripheral surface of the seal seat portion 30b.

  Also in the present embodiment, the grease reservoir 35 includes the radially inner peripheral surface of the flange portion 22, the radially outer peripheral surface of the axially inwardly protruding portion 38, and the axially inner portion of the main body portion 32 therebetween. It is defined by the side surface and can have a large lubricating auxiliary effect.

Since the seal seat portion 30b of the present embodiment configured as described above can be easily disassembled and assembled, the maintainability can be improved.
Other configurations and operations are the same as those in the second embodiment.

(Fourth embodiment)
Next, a full roller type cylindrical roller bearing 20c according to a fourth embodiment will be described with reference to FIG. Note that the full-roller cylindrical roller bearing 20c of this embodiment is different from that of the first embodiment in the configuration of the seal seat portion 30c.

  The seal seat 30c of the present embodiment is provided integrally with the pair of flanges 22 of the outer ring 23 by extending the flanges 22 inward in the radial direction. For this reason, the collar part 22 which comprises the seal seat part 30c has the protrusion part 22d which protrudes toward the axial direction outer side by the protrusion amount B from the axial direction end surface 23a of the outer ring | wheel 23. As shown in FIG.

Therefore, the inner peripheral surface of the flange portion 22 constituting the seal seat portion 30c has an axial length in which the distal end portion 46 of the elastic body 45 is always in sliding contact when the outer ring 23 and the inner ring 25 are relatively displaced in the axial direction. Therefore, even if relative movement between the inner ring 25 and the outer ring 23 is allowed, the sealing performance can be maintained.
Other configurations and operations are the same as those in the first embodiment.

(Fifth embodiment)
Next, a full roller type cylindrical roller bearing 20d according to a fifth embodiment will be described with reference to FIG. In addition, in the full-roller type cylindrical roller bearing 20d of the present embodiment, the configuration of the seal seat portion 30d is different from that of the fourth embodiment.

  Similarly to the seal seat portion 30c of the fourth embodiment, the seal seat portion 30d of the present embodiment is provided integrally with the pair of flange portions 22 of the outer ring 23 by extending the flange portion 22 inward in the radial direction. On the other hand, the flange portion 22 constituting the seal seat portion 30d does not have the protruding portion 22d of the fourth embodiment, and the axial end surface 23a of the outer ring 23 is a flat surface that continues to the inner peripheral surface of the seal seat portion 30d. ing.

Therefore, when the outer ring 23 and the inner ring 25 are relatively displaced in the axial direction on the inner peripheral surface of the flange part 22 constituting the seal seat part 30d, the tip part 46 of the elastic body 45 is always provided without providing the protruding part 22d. As long as it has an axial length that is in sliding contact, the sealing performance can be maintained even when relative movement between the inner ring 25 and the outer ring 23 is allowed. In addition, by designing the outer ring 23 to be wider in the axial direction than the inner ring 25, the outer ring 23 can sufficiently secure an axial length for the distal end portion 46 of the elastic body 45 to be always in sliding contact.
Other configurations and operations are the same as those of the fourth embodiment.

(Sixth embodiment)
Next, a full roller type cylindrical roller bearing 20e according to a sixth embodiment will be described with reference to FIG. In addition, in the full-roller cylindrical roller bearing 20e of this embodiment, the configuration of the cored bar 41b of the seal member 40b is different from that of the first embodiment.

In this embodiment, the metal core 41b of the seal member 40b has an inward flange portion 47 on the inner side in the axial direction than the cylindrical portion 42, and is formed in a substantially crank shape in cross section. The cored bar 41 b is fixed to the inner ring 25 by fitting the distal end portion of the inward flange portion 47 into the fitting groove 25 a while the cylindrical portion 42 is fitted to the outer peripheral surface of the inner ring 25.
Other configurations and operations are the same as those in the first embodiment.

(Seventh embodiment)
Next, a full roller type cylindrical roller bearing 20f according to a seventh embodiment will be described with reference to FIG. Note that the full-roller cylindrical roller bearing 20f of the present embodiment differs from that of the first embodiment in the configuration of the seal member 40f.

In the present embodiment, the distal end portion 46 of the elastic body 45 of the seal member 40f constitutes a non-contact type seal. That is, the pair of seal members 40 f are a core metal 41 attached to the outer peripheral surface of the inner ring 25, and a distal end portion 46 that is provided on the radially outer side of the core metal 41 and faces the inner peripheral surface of the seal seat 30 in close proximity. Each of the elastic bodies 45 is provided.
Even in such a non-contact type seal, the bearing space of the full-roller type cylindrical roller bearing 20f can be sealed, and the amount of grease used can be reduced.
Other configurations and operations are the same as those in the first embodiment.

  In addition, a full-roller cylindrical roller bearing 20g according to a modification of the present embodiment shown in FIG. 10 includes a cylindrical portion 42g fitted to the outer peripheral surface of the inner ring 25 as a sealing member, and an axial end of the cylindrical portion 42g. It may be a shield material 40g having a substantially L-shaped cross section including a flange portion 43g extending in the radial direction from the portion. This shield material 40g is provided with a front end portion 46 that is close to and opposed to the inner peripheral surface of the seal seat 30 and constitutes a non-contact type seal.

(Eighth embodiment)
Next, a full roller type cylindrical roller bearing 20h according to an eighth embodiment will be described with reference to FIG.
In the full-roller type cylindrical roller bearing 20h of the present embodiment, instead of the outer ring 23 having a pair of flange portions 22 as in the above-described embodiment, the inner ring 25 is disposed radially outside the inner ring raceway surface 24 in the axial direction. It has a pair of collar part 27 extended toward the direction.

  For this reason, in the full-roller cylindrical roller bearing 20h of the present embodiment, the pair of seal seat portions 30h are provided separately from the pair of flange portions 27 of the inner ring 25, and the pair of seal members 40h are provided on the outer ring 23. A front end portion 46 that is attached and that is in sliding contact with the outer peripheral surface of the seal seat portion 30h is provided.

  Specifically, the seal seat portion 30 h includes a main body portion 132 having a mounting surface 131 fitted and attached to the outer peripheral surface of the flange portion 27 of the inner ring 25, and a radially outer side of the main body portion 132. And a projecting portion 133 projecting outward in the axial direction from the axially outer side surface 132a. A convex portion 134 is formed on the inner peripheral surface of the main body portion 132, and is positioned in the axial direction by fitting into a groove portion 25 d formed on the outer peripheral surface of the collar portion 27. Further, the seal seat portion 30 h has a grease reservoir portion 135 that is recessed on the inner side surface in the axial direction, and opens to the axial end surface of the cylindrical roller 26.

  The axially outer side surface 132a of the main body 132 is formed flush with the axial end surface 25c of the inner ring 25, and the axially inner side surface 132b of the main body 132 is also the same as the axially inner side surface 27a of the flange portion 27 of the inner ring 25. It is formed flush.

The metal core 141 of the seal member 40h includes a cylindrical portion 142 that fits in a fitting groove 23d formed on the inner peripheral surface of the outer ring 23, and a flange that extends radially inward from the axial end of the cylindrical portion 142. An annular member having a section 143 and having a substantially L-shaped cross section. The elastic body 145 is provided so as to cover the inner diameter portion of the flange portion 143.
Therefore, in this embodiment, the inner ring 25 constitutes one of the track rings of the present invention, and the outer ring 23 constitutes the other track ring.

Thereby, also in this embodiment, the bearing space of the full-roller type cylindrical roller bearing 20h can be sealed, and the amount of grease used can be reduced. Also suitable for supporting the end on the free side by allowing relative movement in the axial direction of the inner ring and outer ring due to the elongation of the inner ring while ensuring the handleability of the bearing and the assembly to the shaft. can do.
In particular, since the elastic body 45 of the seal member 40h presses the seal seat 30h from the radially outer side to the inner side, the seal member 40 attached to the inner ring 25 as in the first embodiment presses the seal seat 30. Compared with this, the pressing force is increased and the sealing performance is further improved.
Other configurations and operations are the same as those in the first embodiment. In addition, a configuration in which a pair of seal seats is provided on each of the pair of flanges 27 of the inner ring 25 and the pair of seal members are attached to the outer ring is also applicable to other embodiments.

In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.
For example, the shape of the distal end portion 46 of the elastic body 45 of the seal member 40 of the present invention, that is, the contact-type lip portion is not limited to that of FIG. 8A shown in the above embodiment, but FIG. -Any shape of the other front-end | tip parts 46a-46h shown in FIG.8 (i) may be sufficient. For example, the slidability of the tip portions 46, 46c to 46h may be improved by reducing the contact area with the inner peripheral surface of the seal seat portion 30 as in the tip portions 46, 46c to 46h. . Moreover, it may be such that it contacts the inner peripheral surface of the seal seat 30 at two places, such as the tip portions 46a, 46c, 46e, 46g, and between the tip portions 46a, 46c, 46e, 46g. The slidability of the tip portions 46a, 46c, 46e, 46g may be improved by pre-filling the recesses 48a, 48c, 48e, 48g provided with grease. Moreover, the garter spring 60 may be provided like the front-end | tip parts 46g and 46h.

  Moreover, in this embodiment, although all embodiment has a symmetrical shape with respect to an axial direction intermediate part, the full roller type cylindrical roller bearing 20 of this invention is not limited to this. For example, one side in the axial direction is configured to have the seal seat portion and the seal member of the present invention, and the other side in the axial direction is configured to have an arbitrary shape, and the bearing space is sealed to reduce the amount of grease used. The relative movement between the inner ring and the outer ring may be allowed.

20, 20 a, 20 b, 20 c, 20 d, 20 e, 20 f, 20 g, 20 h Full roller type cylindrical roller bearings 22, 27 flange 23 outer ring 25 inner ring 26 cylindrical roller 30, 130 seal seat 35, 135 grease reservoir 40, 40 a 40b, 40f, 40g, 40h Seal members 41, 41a, 41b, 141 Core metal 45, 145 Elastic body 46, 146 Tip

Claims (9)

A pair of races comprising an outer ring and an inner ring;
A plurality of cylindrical rollers disposed between both raceway surfaces of the pair of raceways;
With
Of the pair of race rings, one of the race rings has a flange portion extending radially in the axial direction outside of the raceway surface, grease is sealed in a bearing space, and the pair of race rings The bearing ring of this is a full-roller cylindrical roller bearing capable of relative displacement in the axial direction,
A seal seat provided integrally with or separately from the collar,
A seal member that is attached to the other race ring and includes a tip portion that is in sliding contact with or in close proximity to the peripheral surface of the seal seat;
A full-roller type cylindrical roller bearing further comprising:   2. The full complement cylindrical roller bearing according to claim 1, wherein the seal seat protrudes outward in the axial direction from an axial end face of the one raceway ring. The one race ring has a pair of flanges extending in the radial direction outside the raceway surface in the axial direction,
The pair of collars are provided with a pair of seal seats provided integrally or separately, and
The full roller type cylindrical roller bearing according to claim 1, wherein the pair of seal members are provided so that the front end portions are in sliding contact with or in close proximity to the peripheral surfaces of the pair of seal seat portions.   The circumferential surface of the pair of seal seats has an axial length in which the tip end is always in sliding contact or close proximity when the pair of race rings are relatively displaced in the axial direction. 3. A full-roller cylindrical roller bearing according to 3.   The full-roller type cylindrical roller bearing according to any one of claims 1 to 4, wherein the seal seat portion has a grease reservoir portion that is recessed on an inner side surface in an axial direction thereof.   The seal member has a metal core attached to a peripheral surface of the other raceway ring, and a front end portion which is provided on a flange portion of the metal core and is in sliding contact with or in close proximity to the peripheral surface of the seal seat portion. A full-roller cylindrical roller bearing according to any one of claims 1 to 5, further comprising an elastic body.   The metal core of the seal member has a substantially L-shaped cross section including a cylindrical portion that fits to the peripheral surface of the other raceway ring and the flange portion that extends in the radial direction from the axial end portion of the cylindrical portion. The full-roller cylindrical roller bearing according to claim 6, wherein the cylindrical roller bearing is a ring member. Of the pair of race rings of the cylindrical roller bearing, a main body portion having an attachment surface that can be attached to the flange portion of one of the race rings,
It is formed in an annular shape having a protruding portion that protrudes outward in the axial direction from the axial side surface of the main body portion on the other raceway side in the radial direction from the main body portion. Seal seat. A seal seat according to claim 8;
A cored bar that can be attached to the peripheral surface of the other bearing ring of the cylindrical roller bearing, and a tip part that is provided on the flange part of the cored bar and that slidably contacts or closely faces the peripheral surface of the seal seat part. A sealing member comprising an elastic body,
A sealing device comprising:

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