JP2006214469A - Rolling bearing with alignment ring - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve bearing life by preventing heat generation and wear even when creep occurs between an inner diameter recess part spherical surface of an alignment ring and outer diameter convex spherical surface. <P>SOLUTION: In an embodiment (a), large number of pockets 21 which act as oil reservoirs are machined on inner diameter of an alignment ring 12. Consequently, heat generation can be suppressed and wear can be prevented by solid lubricant retained in the pocket 21 by filling the pocket 21 with solid lubricant at a time of assembly even if creep occurs between the inner diameter recess part spherical surface 13 of the alignment ring 12 and an outer diameter convex part spherical surface 14 of the outer ring 2. Also, alignment performance between the inner diameter recess part spherical surface 13 of the alignment ring 12 and the outer diameter convex part spherical surface 14 of the outer ring 2 can be maintained suitably by solid lubricant retained in the pocket 21. In an embodiment of (b), large number of the pockets 21 which act as oil reservoirs are machined on the outer diameter of the outer ring 2. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention supports a rotating shaft such as a central axis of a roll for a rolling mill in which a thrust load is applied in addition to a large radial load, the length of the shaft is large, and deformation (bending) of the shaft due to the load is relatively large. In particular, even when the rotation axis tends to tilt, it prevents local loads such as edge loads from being applied to each component, improving the reliability and durability of the rotation support section The present invention relates to a roller bearing with a centering ring.

  Cylindrical roller bearings, tapered roller bearings, and self-aligning roller bearings with large load capacities are widely used as rolling bearings for incorporation into rotating support parts that support large radial loads such as the center axis of rolling mill rolls. Has been. A cylindrical roller bearing with a centering ring in which a centering ring is provided around an outer ring constituting the cylindrical roller bearing is also known. In the case of a cylindrical roller bearing with an aligning ring, if the center axis of the aligning ring and the center axis of the outer ring tend to be inconsistent, the outer ring and the aligning ring are relatively oscillated and displaced. This prevents local loads such as edge loads from being applied to some cylindrical roller bearings.

  In the case of the conventional rolling bearing as described above, when a thrust load is supported in addition to a large radial load and the rotation shaft tends to tilt, a local load such as an edge load is applied to each component part. It was difficult to prevent this, or it was inevitable that the cost was high.

  First, in the case of general cylindrical roller bearings and tapered roller bearings, the outer ring, the inner ring raceways, and the rolling surfaces of the rollers are all simply cylindrical surfaces or conical curved surfaces, so that the rotation axis is inclined. Edge load is applied to the contact portion between both ends of the rolling surface and both the outer ring and the inner ring raceway. Based on this edge load, excessive contact pressure acts on the contact portion between these rolling surfaces and the outer ring and inner ring raceways, which not only impairs the durability of the roller bearing, but also causes galling in severe cases. It may cause damage such as burn-in.

  In the case of a self-aligning roller bearing, edge load can be prevented and a thrust load of a certain size can be supported. In addition to the possibility of local wear, it is inevitable that the production of spherical rollers is cumbersome and costly. Further, in the case of a cylindrical roller bearing with an aligning ring provided with an aligning ring around the cylindrical roller bearing, there is almost no function of supporting a thrust load. For this reason, when it is used for a rotation support portion that needs to support a very large radial load such as a roll for a rolling mill, the load capacity may be insufficient.

  From such a background, Patent Document 1 uses a double-row tapered roller bearing with a centering mechanism. In other words, double-row tapered roller bearings with a centering mechanism support a large thrust load in addition to a large radial load, and even when the rotating shaft tends to tilt, local loads such as edge loads are applied to each component part. A structure capable of preventing the addition can be obtained at a low cost.

  The double-row tapered roller bearing with a centering mechanism includes one outer ring, a pair of inner rings, a plurality of tapered rollers, and a centering ring. Of these, the outer ring forms a double-row outer ring raceway on the inner peripheral surface. Each of these outer ring raceways has a conical concave shape and is inclined in directions opposite to each other, and in a direction in which the inner diameter increases toward each opening. Further, the pair of inner rings form conical convex inner ring raceways on their outer peripheral surfaces. The pair of inner rings formed in this way are arranged inside the outer ring with the end faces on the small diameter side of each inner ring raceway facing each other. A plurality of tapered rollers are provided between each outer ring raceway and each inner ring raceway. Further, the aligning ring is arranged around the outer ring. The inner peripheral surface of the aligning ring is a spherical concave surface centered on a point on the center axis of the aligning ring, and the outer peripheral surface of the outer ring is a spherical surface centered on a point on the center axis of the outer ring. Convex surface. A centering function is provided by fitting the inner peripheral surface of these aligning rings and the outer peripheral surface of the outer ring to the swinging displacement of these aligning wheels and the outer ring without looseness. .

  According to the double-row tapered roller bearing with the alignment mechanism configured as described above, it is possible to support a thrust load in addition to a large radial load. That is, since the plurality of tapered rollers are arranged in a double row, the radial load capacity of the plurality of tapered rollers can be increased. Even when a thrust load is applied between the outer ring and the inner ring, the tapered load in any row is sandwiched between the outer ring raceway and the inner ring raceway in the thrust direction to support the thrust load. In addition, when the rotating shaft that externally supports the pair of inner rings tends to be inclined with respect to the housing that internally supports the aligning ring, the outer ring may swing and displace inside the aligning ring. Thus, the inclination is compensated, and the center axis of the outer ring and the center axis of the inner ring are kept matched. As a result, local load such as edge load is formed on the outer ring raceway on the inner peripheral surface of the outer ring and the contact portion between the inner ring raceway on the outer peripheral surface of the inner ring and the rolling surface of each tapered roller, which constitutes the main body portion of the double row tapered roller bearing. Can be prevented from being added. Moreover, since the tapered roller constituting this structure is a simple tapered surface with a rolling surface, the production is not troublesome as the spherical roller constituting the self-aligning roller bearing. Therefore, production costs are not increased.

  In Patent Document 2, a roller bearing with an aligning ring in which a plurality of rollers are rotatably provided between an outer ring and an inner ring and the outer ring is swingably fitted to the aligning ring. An oil groove or pocket serving as an oil reservoir is provided in at least one of the inner surface concave spherical surface of the core ring and the outer diameter convex spherical surface of the outer ring.

Accordingly, in Patent Document 2, when oil or grease is applied to these oil grooves or pockets when assembled, creep occurs between the inner surface concave spherical surface of the aligning ring and the outer diameter convex spherical surface of the outer ring. However, heat generation can be suppressed and wear can be prevented.
Japanese Patent Laid-Open No. 10-220467 Japanese Patent Application No. 2004-301852

  However, in Patent Document 1, in the case of a double-row tapered roller bearing with a centering mechanism, depending on use conditions, when creep occurs between the inner surface concave spherical surface of the aligning ring and the outer diameter convex spherical surface of the outer ring, Heat generation and wear increase, which may lead to bearing damage. Here, creep refers to a phenomenon of relative displacement between the mating surfaces.

  Further, in Patent Document 2, lubricating oil or grease is applied to an oil groove or pocket serving as an oil reservoir, but the lubricating oil or grease flows out from the oil groove or pocket, resulting in lubrication. There may be a shortage of oil or grease.

  The present invention has been made in view of the circumstances as described above, and during use, even when creep occurs between the inner surface concave spherical surface of the aligning ring and the outer diameter convex spherical surface of the outer ring during use, An object of the present invention is to provide a roller bearing with a centering ring that can significantly improve the life of the bearing by reliably preventing heat generation and wear.

In order to achieve the above object, a roller bearing with an aligning ring according to claim 1 of the present invention is provided with a plurality of rollers movably interposed between an outer ring and an inner ring so that the outer ring can swing. In roller bearings with aligning rings that are fitted to aligning rings,
At least one of the inner surface concave spherical surface of the aligning ring and the outer diameter convex spherical surface of the outer ring is provided with an oil groove or pocket serving as an oil reservoir,
The oil groove or pocket is filled with a solid lubricant.

  According to the present invention, at least one of the inner diameter concave spherical surface of the aligning ring and the outer diameter convex spherical surface of the outer ring is provided with an oil groove or pocket serving as an oil reservoir, and the oil groove or pocket has a solid shape. Filled with lubricant.

  Therefore, even when creep occurs between the inner surface concave spherical surface of the aligning ring and the outer surface convex spherical surface of the outer ring, the solid lubricant held in the oil groove or pocket suppresses heat generation and wear. Can be prevented, and the bearing life can be remarkably improved.

  Moreover, the alignment between the inner surface concave spherical surface of the aligning ring and the outer diameter convex spherical surface of the outer ring can be maintained well by the solid lubricant held in the oil groove or pocket.

  Furthermore, in Patent Document 2, lubricating oil or grease may flow out from an oil groove or pocket serving as an oil reservoir.

  However, as in the present invention, if filled with a solid lubricant, it will not flow out, and when sufficient lubricating oil or grease does not spread between the aligning rings, Even when creep occurs between the outer ring and the outer surface of the outer ring, the oil oozes out from the solid lubricant to suppress heat generation and prevent wear, thereby significantly improving the bearing life. Can do.

  Furthermore, by machining the oil groove or pocket to both ends of each part, even if the solid lubricant retained in the oil groove or pocket flows out, lubrication of the bearing from both ends of the oil groove By entering the oil, even if creeping between the inner surface concave spherical surface of the aligning ring and the outer diameter convex spherical surface of the outer ring, heat generation can be suppressed and wear can be prevented, and the bearing life can be significantly improved. Can do.

  Hereinafter, a roller bearing with a centering ring according to an embodiment of the present invention will be described with reference to the drawings.

(Double-row tapered roller bearing with alignment mechanism to which the present invention is applied)
FIG. 1 is a cross-sectional view of a double row tapered roller bearing with a centering mechanism to which the present invention is applied.

  The double-row tapered roller bearing 1 with a centering mechanism includes a single outer ring 2, a pair of inner rings 3 and 3, a plurality of tapered rollers 4 and 4, and a single aligning ring 12. Of these, the outer ring 2 has double-row outer ring raceways 5 and 5 formed on the inner peripheral surface. Each of the outer ring raceways 5 and 5 has a conical concave shape, and is inclined in directions opposite to each other and in a direction in which the inner diameter becomes larger toward the opening. Therefore, the inner diameter of the outer ring 2 is the smallest at the center and gradually increases toward the openings at both ends.

  The pair of inner rings 3 and 3 form conical convex inner ring raceways 6 and 6 on their outer peripheral surfaces. Further, an outer flange-like large-diameter side flange portion 7 is also provided on the outer peripheral surface of one end portion (left and right end portions in FIG. 1) of each inner ring 3, 3 at the large-diameter side end portion of the inner ring raceway 6. On the outer peripheral surface of the other end portion (center end portion in FIG. 1), a small-diameter side flange portion 8 having an outward flange shape is also formed at a portion located at the small-diameter side end portion of the inner ring raceway 6. The pair of inner rings 3 and 3 formed in this way are arranged in such a manner that the end faces on the small diameter side of the inner ring raceways 6 and 6, that is, the small diameter side flanges 8 and 8 face each other. It is arranged inside. In the illustrated example, a spacer 9 is sandwiched between the end faces of the pair of inner rings 3 and 3.

  Further, a plurality of tapered rollers 4 and 4 can be freely rolled into respective pockets (not shown) of the cages 10 and 10 between the outer ring raceways 5 and 5 and the inner ring raceways 6 and 6, respectively. It is provided in the state held in

  Further, the aligning ring 12 is disposed around the outer ring 2. The inner peripheral surface 13 of the aligning ring 12 is a spherical concave surface having a point O on the center axis X of the aligning ring 12 as its center. The outer peripheral surface 14 of the outer ring 2 is also a spherical convex surface with the point O on the central axis X of the outer ring 2 as its center. In the illustrated example, each of these points O is provided at the center position in the axial direction of the aligning ring 12 and the outer ring 2.

  Accordingly, the inner diameter of the inner peripheral surface 13 (inner diameter concave spherical surface) and the outer diameter of the outer peripheral surface 14 (outer diameter convex spherical surface) are the largest at the axial center of the aligning ring 12 or outer ring 2. Note that the radii of curvature of the inner peripheral surface 13 (inner diameter concave spherical surface) and the outer peripheral surface 14 (outer diameter convex spherical surface) are equal to each other. The outer peripheral surface of the aligning ring 12 is a simple cylindrical surface.

  The aligning ring 12 and the outer ring 2 in which both inner and outer peripheral surfaces are formed as described above are the inner peripheral surface 13 (inner diameter concave spherical surface) of the aligning ring 12 and the outer peripheral surface 14 (outer diameter convex spherical surface of the outer ring 2). ), And the centering ring 12 and the outer ring 2 can be freely oscillated and displaced without looseness.

  According to the double row tapered roller bearing 1 with the alignment mechanism configured as described above, it is possible to support a thrust load in addition to a large radial load. That is, since the plurality of tapered rollers 4 and 4 are arranged in a double row, the load capacity in the radial direction by the plurality of tapered rollers 4 and 4 can be increased. Further, even when a thrust load is applied between the outer ring 2 and the inner rings 3, 3, the tapered roller 4 in any row has a thrust direction between any outer ring raceway 5 and any inner ring raceway 6. Thrust load is supported by being pinched by

  Further, when a rotation shaft (not shown) that supports the fitting of the pair of inner rings 3 and 3 tends to be inclined with respect to the housing (not shown) that supports the fitting of the aligning ring 12, this alignment is performed. The outer ring 2 is oscillated and displaced inside the ring 12. Then, based on this swing displacement, the inclination is compensated so that the central axis of the outer ring 2 and the central axes of the pair of inner rings 3 and 3 remain in alignment. As a result, the outer ring raceways 5 and 5 provided on the inner peripheral surface of the outer ring 2 and the inner ring raceways 6 and 6 provided on the outer peripheral surfaces of the inner rings 3 and 3 constituting the main body portion of the double row tapered roller bearing 1 with the aligning mechanism. And it can prevent that local load, such as an edge load, is added to the contact part with the rolling surface of each tapered roller 4,4.

  Moreover, since the tapered rollers 4 and 4 constituting the double row tapered roller bearing 1 with a centering mechanism are simple tapered surfaces, spherical rollers constituting a conventionally known spherical roller bearing are known. The production is not troublesome. Therefore, production costs are not increased.

(First embodiment)
FIG. 2A is a half sectional view of the aligning ring according to the first embodiment of the present invention, and FIG. 2B is a half sectional view of the outer ring.

  In the example of FIG. 2A, a large number of pockets 21 serving as oil reservoirs are processed on the inner diameter of the aligning ring 12.

  Thereby, even if creep occurs between the inner surface concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 by filling the pocket 21 with a solid lubricant at the time of incorporation, the pocket 21 The solid lubricant held in 21 can suppress heat generation, prevent wear, and can significantly improve the bearing life.

  In addition, the alignment between the inner surface concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 can be favorably maintained by the solid lubricant held in the pocket 21.

  Furthermore, in patent document 2, lubricating oil and grease may flow out from the pocket 21 which becomes an oil reservoir.

  However, as in the present embodiment, if the pocket 21 is filled with a solid lubricant, the pocket 21 will not flow out. Even when creep occurs between the inner surface concave spherical surface 13 of the ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2, exudation of oil from the solid lubricant suppresses heat generation and prevents wear. The bearing life can be remarkably improved.

  The solid lubricant may be, for example, a mixture of a base oil and a resin, a resin or a porous body impregnated with a base oil, or a solid base oil (for example, wax) at room temperature. it can. The type of base oil of the solid lubricant is not particularly limited and may be a problem if it is generally used as a lubricant base oil, such as mineral oil, synthetic hydrocarbon oil, ether oil, etc. It can be used without.

  However, the base oil of the solid lubricant and the base oil of the lubricant inside the bearing are preferably the same type. That is, it is preferable to use the same kind of mineral oil or the same kind of synthetic hydrocarbon oil. Furthermore, it is more preferable if the kinematic viscosities are the same.

  Here, the solid lubricant formed by mixing the base oil and the resin will be described in detail. Such solid lubricants include polyolefin resins such as polyethylene, polypropylene, polybutylene and polymethylpentene, paraffinic hydrocarbon oils (for example, poly α-olefin oils), naphthenic hydrocarbon oils, mineral oils, ether oils ( For example, a raw material obtained by mixing a base oil such as dialkyl diphenyl ether oil) or ester oil (eg, phthalate ester) may be used alone or in combination of two or more. It is plasticized by heating to the above, and then solidified by cooling. The solid lubricant may contain various additives such as an antioxidant, a rust inhibitor, an antiwear agent, a foam remover, and an extreme pressure agent.

  The composition ratio between the polyolefin resin and the base oil in the solid lubricant is preferably 10 to 50% by mass of the polyolefin resin and 90 to 50% by mass of the base oil. If the polyolefin resin is less than 10% by mass, the hardness and strength of the solid lubricant may be insufficient, and the initial shape should be maintained when a load or vibration is applied due to rotation of the bearing. Is difficult, and there is a high possibility that problems such as detachment from the groove occur. On the other hand, when the amount of the polyolefin-based resin exceeds 50% by mass (that is, when the base oil is less than 50% by mass), the supply amount of the base oil to the bearing decreases, and the effect may not be obtained.

  Polyolefin resins usually have various average molecular weights (the basic structure is the same), and the physical properties may differ depending on the average molecular weight. Therefore, a raw material resin having desired physical properties can be prepared by mixing resins having various average molecular weights as required.

For example, those classified as waxes having an average molecular weight of 700 to 1 × 10 ⁴ (for example, polyethylene wax), those having a relatively low molecular weight of 1 × 10 ⁴ to 1 × 10 ⁶ and those having an average molecular weight of 1 × 10 ^{6 to} 5 × 10 ⁶ ultrahigh molecular weight.

  A solid lubricant having a certain degree of mechanical strength, base oil supply capability, and oil retention can be obtained by combining a base oil with a relatively low molecular weight. If some of the relatively low molecular weight substances are replaced with those classified as waxes, the difference in molecular weight between those classified as waxes and the base oils is small, which increases the affinity with the base oils. As a result, the oil retention of the solid lubricant is improved, and the base oil can be supplied for a longer period. However, on the other hand, the mechanical strength tends to decrease. As the wax, in addition to a polyolefin resin such as polyethylene wax, a hydrocarbon wax having a melting point in the range of 100 to 130 ° C. or higher (for example, a paraffin synthetic wax) can be used.

  On the other hand, if a part of the relatively low molecular weight is replaced with an ultra-high molecular weight, the difference in molecular weight between the ultra-high molecular weight and the base oil is large, so the affinity with the base oil decreases, As a result, the oil retaining property tends to decrease. As a result, the speed at which the base oil exudes from the solid lubricant is increased, that is, the time until all the base oil exudes from the solid lubricant is shortened, and the life of the bearing is shortened. However, the mechanical strength is improved.

  Considering the balance of moldability, mechanical strength, oil retention, and base oil supply amount, the composition ratio of the solid lubricant is 0-5% by mass classified as wax, and 8 having a relatively low molecular weight. It is preferable that ˜48 mass%, ultrahigh molecular weight one is 2 to 15 mass%, and the total of the three types is 10 to 50 mass% (the balance is base oil).

The solid lubricant preferably has a hardness [HD _A ] in the range of 65 to 90, which is one measure of mechanical strength. When the hardness [HD _A ] is less than 65, the strength is not sufficient and the solid lubricant may be damaged by the rotation of the bearing. On the other hand, when the hardness [HD _A ] exceeds 90, the mechanical influence on the rolling elements that come into contact increases, thereby increasing the torque of the bearing or increasing the heat generated by the rotation of the bearing. The temperature of the battery may become high. In order to make it difficult for such problems to occur, the hardness [HD _A ] is more preferably in the range of 70 to 85.

  The same applies to other embodiments described below.

  In the example of FIG. 2B, a large number of pockets 21 serving as oil reservoirs are processed on the outer diameter of the outer ring 2.

  Thereby, even if creep occurs between the inner surface concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 by filling the pocket 21 with a solid lubricant at the time of incorporation, the pocket 21 The solid lubricant held in 21 can suppress heat generation, prevent wear, and can significantly improve the bearing life.

  In addition, the alignment between the inner surface concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 can be favorably maintained by the solid lubricant held in the pocket 21.

  Furthermore, in patent document 2, lubricating oil and grease may flow out from the pocket 21 which becomes an oil reservoir.

  However, as in the present embodiment, if the pocket 21 is filled with a solid lubricant, the pocket 21 will not flow out. Even when creep occurs between the inner surface concave spherical surface 13 of the ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2, exudation of oil from the solid lubricant suppresses heat generation and prevents wear. The bearing life can be remarkably improved.

  The pocket shape is not limited to a quadrangle (shown in FIG. 2), and may be a circle, an ellipse, or a polygon.

(Second Embodiment)
FIG. 3 is a half sectional view of the aligning ring according to the second embodiment of the present invention.

  In the present embodiment, a large number of oil grooves 22 serving as oil reservoirs are processed in the inner diameter of the aligning ring 12. The oil groove 22 is formed in a rectangular shape extending in the axial direction.

  Thereby, even when creep occurs between the inner diameter concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 by filling the oil groove 22 with a solid lubricant when assembled, The solid lubricant held in the oil groove 22 can suppress heat generation, prevent wear, and can significantly improve the bearing life.

  In addition, the alignment between the inner surface concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 can be well maintained by the solid lubricant held in the oil groove 22.

  Furthermore, in Patent Document 2, lubricating oil or grease may flow out from the oil groove 22 that becomes an oil reservoir.

  However, if the oil groove 22 is filled with a solid lubricant as in the present embodiment, the oil groove 22 will not flow out, and when the lubricating oil or grease does not spread sufficiently between the aligning rings 12, Even when creep occurs between the inner surface concave spherical surface 13 of the core ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2, exudation of oil from the solid lubricant suppresses heat generation and prevents wear. The bearing life can be remarkably improved.

  An oil groove 22 may be formed in the outer diameter convex spherical surface 14 of the outer ring 2.

(Third embodiment)
FIG. 4 is a half sectional view of the aligning ring according to the third embodiment of the present invention.

  In the present embodiment, a large number of oil grooves 22 serving as oil reservoirs are processed in the inner diameter of the aligning ring 12. The oil groove 22 is formed extending in the circumferential direction.

  Thereby, even when creep occurs between the inner diameter concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 by filling the oil groove 22 with a solid lubricant when assembled, The solid lubricant held in the oil groove 22 can suppress heat generation, prevent wear, and can significantly improve the bearing life.

  In addition, the alignment between the inner surface concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 can be well maintained by the solid lubricant held in the oil groove 22.

  Furthermore, in Patent Document 2, lubricating oil or grease may flow out from the oil groove 22 that becomes an oil reservoir.

  However, if the oil groove 22 is filled with a solid lubricant as in the present embodiment, the oil groove 22 will not flow out, and when the lubricating oil or grease does not spread sufficiently between the aligning rings 12, Even when creep occurs between the inner surface concave spherical surface 13 of the core ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2, exudation of oil from the solid lubricant suppresses heat generation and prevents wear. The bearing life can be remarkably improved.

  An oil groove 22 may be formed in the outer diameter convex spherical surface 14 of the outer ring 2.

(Fourth embodiment)
FIG. 5A is a half sectional view of the aligning ring according to the fourth embodiment of the present invention, and FIG. 5B is a half sectional view of the aligning ring according to the modification.

  In the present embodiment shown in FIG. 5A, a large number of oil grooves 22 serving as oil reservoirs are processed on the inner diameter of the aligning ring 12. The oil groove 22 is formed in a well shape extending in the axial direction and the circumferential direction.

  Thereby, even when creep occurs between the inner diameter concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 by filling the oil groove 22 with a solid lubricant when assembled, The solid lubricant held in the oil groove 22 can suppress heat generation, prevent wear, and can significantly improve the bearing life.

  In addition, the alignment between the inner surface concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 can be well maintained by the solid lubricant held in the oil groove 22.

  Furthermore, in Patent Document 2, lubricating oil or grease may flow out from the oil groove 22 that becomes an oil reservoir.

  However, if the oil groove 22 is filled with a solid lubricant as in the present embodiment, the oil groove 22 will not flow out, and when the lubricating oil or grease does not spread sufficiently between the aligning rings 12, Even when creep occurs between the inner surface concave spherical surface 13 of the core ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2, exudation of oil from the solid lubricant suppresses heat generation and prevents wear. The bearing life can be remarkably improved.

  An oil groove 22 may be formed in the outer diameter convex spherical surface 14 of the outer ring 2.

  In the modification shown in FIG. 5B, a large number of oil grooves 22 serving as oil reservoirs are processed on the inner diameter of the aligning ring 12. The oil groove 22 is formed in a well shape that extends obliquely.

  Thereby, even when creep occurs between the inner diameter concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 by filling the oil groove 22 with a solid lubricant when assembled, The solid lubricant held in the oil groove 22 can suppress heat generation, prevent wear, and can significantly improve the bearing life.

  In addition, the alignment between the inner surface concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 can be well maintained by the solid lubricant held in the oil groove 22.

  Furthermore, in Patent Document 2, lubricating oil or grease may flow out from the oil groove 22 that becomes an oil reservoir.

  However, if the oil groove 22 is filled with a solid lubricant as in the present embodiment, the oil groove 22 will not flow out, and when the lubricating oil or grease does not spread sufficiently between the aligning rings 12, Even when creep occurs between the inner surface concave spherical surface 13 of the core ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2, exudation of oil from the solid lubricant suppresses heat generation and prevents wear. The bearing life can be remarkably improved.

  An oil groove 22 may be formed in the outer diameter convex spherical surface 14 of the outer ring 2.

(Fifth embodiment)
FIG. 6A is a half sectional view of the aligning ring according to the fifth embodiment of the present invention, and FIG. 6B is a half sectional view of the aligning ring according to the modification.

  In the present embodiment shown in FIG. 6A, a large number of oil grooves 22 serving as oil reservoirs are processed on the inner diameter of the aligning ring 12. The oil groove 22 is formed in a spiral shape.

  Thereby, even when creep occurs between the inner diameter concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 by filling the oil groove 22 with a solid lubricant when assembled, The solid lubricant held in the oil groove 22 can suppress heat generation, prevent wear, and can significantly improve the bearing life.

  In addition, the alignment between the inner surface concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 can be well maintained by the solid lubricant held in the oil groove 22.

  Furthermore, in Patent Document 2, lubricating oil or grease may flow out from the oil groove 22 that becomes an oil reservoir.

  However, if the oil groove 22 is filled with a solid lubricant as in the present embodiment, the oil groove 22 will not flow out, and when the lubricating oil or grease does not spread sufficiently between the aligning rings 12, Even when creep occurs between the inner surface concave spherical surface 13 of the core ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2, exudation of oil from the solid lubricant suppresses heat generation and prevents wear. The bearing life can be remarkably improved.

  An oil groove 22 may be formed in the outer diameter convex spherical surface 14 of the outer ring 2.

  In the modified example of FIG. 6B, a large number of oil grooves 22 serving as oil reservoirs are processed on the inner diameter of the aligning ring 12.

  The oil groove 22 is formed in a spiral shape, and in addition, by processing the oil groove 22 to both ends of each component (aligning ring 12), a solid lubricant held in the oil groove 22 Even when the oil flows out, creeping is caused between the inner surface concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 by the bearing lubricating oil entering from both ends of the oil groove 22. However, heat generation can be suppressed, wear can be prevented, and bearing life can be significantly improved.

  In addition, by filling the oil groove 22 with a solid lubricant at the time of incorporation, even if creep occurs between the inner diameter concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2, The solid lubricant held in the groove 22 can suppress heat generation, prevent wear, and can significantly improve the bearing life.

  Furthermore, the alignment between the inner diameter concave spherical surface 13 of the aligning ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2 can be well maintained by the solid lubricant held in the oil groove 22.

  Furthermore, in Patent Document 2, lubricating oil or grease may flow out from the oil groove 22 that becomes an oil reservoir.

  However, if the oil groove 22 is filled with a solid lubricant as in the present embodiment, the oil groove 22 will not flow out, and when the lubricating oil or grease does not spread sufficiently between the aligning rings 12, Even when creep occurs between the inner surface concave spherical surface 13 of the core ring 12 and the outer diameter convex spherical surface 14 of the outer ring 2, exudation of oil from the solid lubricant suppresses heat generation and prevents wear. The bearing life can be remarkably improved.

  An oil groove 22 may be formed in the outer diameter convex spherical surface 14 of the outer ring 2.

  Further, also in the second embodiment (FIG. 3) and the fourth embodiment (FIGS. 5A and 5B) described above, the oil groove 22 is provided at both ends of each component (for example, the aligning ring 12). May be processed.

(Shape of oil groove or pocket)
7A, 7B, and 7C are schematic views showing the cross-sectional shapes of the oil grooves or pockets, respectively.

  The cross-sectional shape of the oil groove 22 or the pocket 21 may be a quadrangular shape as shown in FIG. 7A, an arc shape (R shape) as shown in FIG. Thus, it may be triangular, and may be other circles or polygons, and the cross-sectional shape is not limited.

(Cylinder roller bearing with aligning mechanism to which the present invention is applied)
FIG. 8 is a sectional view of a cylindrical roller bearing with a centering mechanism to which the present invention is applied.

  The application target of the present invention is not limited to the double-row tapered roller bearing with the aligning mechanism, and can be applied to other roller bearings with the aligning ring such as the cylindrical roller bearing with the aligning mechanism.

  For example, in a rolling machine of a continuous casting facility, in order to absorb bending of a roll that occurs during rolling of a steel plate or the like, the free side of the roll is supported by a cylindrical roller bearing with an aligning ring having alignment properties.

  FIG. 8 illustrates a full-roller type cylindrical roller bearing with a centering ring. This bearing supports, for example, the free side of a roll of a rolling mill, and an outer ring 32 having an inner ring 31 fitted to a roll (not shown) and a spherical outer diameter surface 32a (outer diameter convex spherical surface). And a plurality of cylindrical rollers 33 interposed between the inner ring 31 and the outer ring 32, and a spherical inner diameter that is fitted into the bearing housing and into which the outer diameter surface 32a (outer diameter convex spherical surface) of the outer ring 32 is fitted. And a centering ring 34 having a surface 34a (inner diameter concave spherical surface).

  Both ends of the outer ring 32 are provided with flanges 32b, and the cylindrical rollers 33 are contacted and guided by both flanges 32b of the outer ring 32 when the bearing rotates. Further, when the roll is bent, the outer ring 32 is aligned and tilted with respect to the aligning ring 34, and the roll is absorbed.

  In addition, this invention is not limited to embodiment mentioned above, A various deformation | transformation is possible.

It is sectional drawing of the double row tapered roller bearing with a centering mechanism used as the application object of this invention. (A) is related to 1st Embodiment of this invention, and is a half sectional view of a centering ring, (b) is a half sectional view of an outer ring. FIG. 7 is a half sectional view of a centering ring according to a second embodiment of the present invention. FIG. 6 is a half sectional view of a centering ring according to a third embodiment of the present invention. (A) is a half cross-sectional view of the aligning ring according to the fourth embodiment of the present invention, and (b) is a half cross-sectional view of the aligning ring according to the modification. (A) is a half cross-sectional view of the aligning ring according to the fifth embodiment of the present invention, and (b) is a half cross-sectional view of the aligning ring according to the modification. (A) (b) (c) is a schematic diagram which shows the cross-sectional shape of an oil groove or a pocket, respectively. It is sectional drawing of the cylindrical roller bearing with a centering mechanism used as the application object of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Double row tapered roller bearing with alignment mechanism 2 Outer ring 3 Inner ring 4 Tapered roller 5 Outer ring raceway 6 Inner ring raceway 7 Large diameter side flange 8 Small diameter side flange 9 Spacer 10 Cage 12 Alignment ring 13 Inner circumferential surface (inner diameter Concave spherical surface)
14 Outer peripheral surface (spherical spherical surface with outer diameter)
21 Pocket 22 Oil groove 31 Inner ring 31
32 Outer ring 32a Outer diameter surface (outer diameter convex spherical surface)
32b flange 33 cylindrical roller 34 aligning ring 34a inner diameter surface (inner diameter concave spherical surface)

Claims (1)

In a roller bearing with an aligning ring in which a plurality of rollers are interposed between the outer ring and the inner ring so as to be able to roll, and the outer ring is slidably fitted to the aligning ring.
At least one of the inner surface concave spherical surface of the aligning ring and the outer diameter convex spherical surface of the outer ring is provided with an oil groove or pocket serving as an oil reservoir,
A roller bearing with a centering ring, wherein the oil groove or pocket is filled with a solid lubricant.

Images