JP2006097764A - Collared cylindrical roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a collared cylindrical roller bearing for suppressing the significant wear of an abutting portion between the axial end face of the cylindrical roller and the inside face of a collar or significant temperature rise at the abutting portion, when subjected to great axial load. <P>SOLUTION: Pockets 10a, 10a of a cage 5a are inclined to a virtual line α parallel to the center axis of the cage 5a. The direction of the inclination is such that, when an outer ring and an inner ring constituting the collared cylindrical roller bearing are relatively rotated, axial force given from cylindrical rollers held in the pockets 10a, 10a to the inner ring is directed opposite to axial load given from the outside to the inner ring. This construction counterbalances or reduces the axial load and suppresses the rise of contact pressure at the abutting portion. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The cylindrical roller bearing with a flange according to the present invention is, for example, a radial load at the time of use, such as a support shaft fixed at the end of a roll for a rolling mill or a rotary shaft fixed with a helical gear constituting a gear transmission device. In addition to this, it is used to rotatably support a rotating shaft to which an axial load is applied to a fixed part such as a housing.

  In addition to the radial load, when using the support shaft fixed at the end of the roll for rolling mills and the rotary shaft fixed to the helical gear that constitutes the gear transmission for driving the railway vehicle, A load is applied. Therefore, a rolling bearing for rotatably supporting these rotary shafts with respect to the housing must be capable of supporting not only radial loads but also axial loads. For this purpose, a flanged cylindrical roller bearing 1 as shown in FIG. 4 is conventionally used. This flanged cylindrical roller bearing 1 is called an NJ type, and can support not only a radial load but also an axial load.

  That is, the flanged cylindrical roller bearing 1 includes an inner ring 2, an outer ring 3, a plurality of cylindrical rollers 4 and 4, and a cage 5. Of these, the inner ring 2 is provided with a cylindrical inner ring raceway 6 at the intermediate portion of the outer peripheral surface, and an outward flange 7 at one end (the left end in FIG. 4). Further, the outer ring 3 is provided with a cylindrical outer ring raceway 8 at an intermediate portion of the inner peripheral surface, and inward flanges 9 and 9 are also provided at both ends. The cylindrical rollers 4 and 4 are provided between the inner ring raceway 6 and the outer ring raceway 8 so as to roll freely. The cage 5 is formed in a cylindrical shape as a whole, and has pockets 10 and 10 for holding the cylindrical rollers 4 and 4 so as to roll freely at a plurality of locations in the circumferential direction, as shown in FIG. The pockets 10 and 10 are formed in parallel to the central axis of the cage 5.

As shown in FIG. 4, the flanged cylindrical roller bearing 1 configured as described above is configured such that the inner ring 2 is fitted and fixed to the rotating shaft 11 and the outer ring 3 is fitted and fixed to the housing 12. The rotary shaft 11 is rotatably supported with respect to the housing 12, and at the same time, an axial load acting on the rotary shaft 11 can be supported. That is, the flanged cylindrical roller bearing 1 has both end surfaces in the axial direction of the cylindrical rollers 4 and 4 on inner side surfaces 13 and 13 of the outward flange portion 7 and the pair of inward flange portions 9 and 9, respectively. Axial loads can be supported between the cylindrical rollers 4 and 4 and the flanges 7 and 9 so as to face each other. In the case of the illustrated example, only one end side of the outer peripheral surface of the inner ring 2 (the left side in FIG. 4), because it has provided the outward flange portion 7, can only be supported axial load F _a acting from the one end It is. In the case of the structure shown in FIG. 4, the flanges 7 and 9 can prevent the cylindrical rollers 4 and 4 from protruding from the inner ring raceway 6 and the outer ring raceway 8.

For the flanged cylindrical roller bearing 1, as described above, it is supported the axial load F _a by the engagement between the cylindrical rollers 4 and 4 and the flanges 7 and 9. Therefore, when the axial load F _a acting on the flanged cylindrical roller bearing 1 is large, the inner surfaces 13, 13 of the axial end surface and the respective flange portions 7, 9 of each cylindrical roller 4, 4 It is easy to cause remarkable wear at the abutting portion, and the temperature at the abutting portion is remarkably increased. Then, there is a possibility that seizure occurs early due to such remarkable wear and temperature rise.

  Patent Document 1 describes a structure in which the cylindrical rollers held in the pockets are skewed to prevent the cage from moving in the axial direction by inclining the pockets of the cage. However, the structure described in Patent Document 1 is intended for N, NU, NNU, and NN type flanged cylindrical roller bearings that are not premised on supporting an axial load.

Japanese Patent Application Laid-Open No. 8-200434

  In view of the circumstances as described above, the flanged cylindrical roller bearing of the present invention has a structure capable of supporting an axial load, and even when a large axial load is applied, the axial end surface of the cylindrical roller and the inner surface of the flange portion The present invention has been invented to realize a structure capable of suppressing the occurrence of significant wear at the abutting portion and the remarkable increase in temperature at the abutting portion.

The flanged cylindrical roller bearing of the present invention includes an outer ring, an inner ring, a plurality of cylindrical rollers, a retainer, and a flange, as in the conventional structure shown in FIG.
Of these, the outer ring has a cylindrical outer ring raceway on the inner peripheral surface.
The inner ring has a cylindrical inner ring raceway on the outer peripheral surface.
Each of the cylindrical rollers is provided between the inner ring raceway and the outer ring raceway so as to roll freely.
The retainer has pockets for rotatably holding the cylindrical rollers at a plurality of locations in the circumferential direction.
The flange portion is integrated with the outer ring and the inner ring at least in the axially opposite ends of the inner ring raceway and the outer ring raceway at the inner ring raceway and the outer ring raceway. Or it is provided in a separate body, and the inner surface thereof is opposed to the axial end surface of each cylindrical roller.
An axial load can be supported based on the engagement between the inner side surface of each flange and the axial end surface of each cylindrical roller.
The “cylindrical roller” includes a “needle”.

  In particular, in the flanged cylindrical roller bearing of the present invention, the pockets are inclined in the same direction with respect to the circumferential direction with respect to an imaginary line parallel to the central axis of the cage. The inclination direction is determined by the axial force that acts on the outer ring or the inner ring from the cylindrical rollers held in the pockets when the outer ring and the inner ring rotate relative to each other. The direction is opposite to the axial load acting on the surface.

  In the case of the present invention configured as described above, the cylindrical rollers respectively held in the pockets of the cage are always skewed. For this reason, when the outer ring and the inner ring are relatively rotated, a force in the axial direction acts on the outer ring or the inner ring from the cylindrical rollers. In the case of the present invention, since this direction is the direction opposite to the axial load acting on the outer ring or the inner ring from the outside, this axial load can be offset or reduced. As a result, even if a large axial load is applied to the flanged cylindrical roller bearing, it is possible to suppress an increase in contact pressure at each contact portion between the axial end surface of each cylindrical roller and the inner surface of each flange portion. And it can suppress that remarkable abrasion arises in each of these contact parts, or the temperature in each of these contact parts raises remarkably, and it can prevent that the said cylindrical roller bearing with a flange | sticking arises at an early stage.

When the present invention is implemented in a general cylindrical roller bearing with a flange incorporated in, for example, a helical gear box, the inclination angle of each pocket is set to the center of the cage as described in claim 2. The angle is preferably 0.6 to 1.3 ° (more preferably 0.6 to 0.9 °) with respect to a virtual line parallel to the axis.
More preferably, as described in claim 3, a mark for identifying the rotational direction is provided on a part of the cylindrical roller bearing with a flange. For example, an arrow indicating the rotational direction is imprinted on the axial end surface of the outer ring or the inner ring.
If comprised in this way, the incorrect assembly | attachment to a rotation support part can be prevented, and the effect of this invention can be acquired reliably.

  1 and 2 show an embodiment of the present invention. The feature of the present invention is that by devising the shape of each pocket 10a, 10a of the cage 5a, a force in the axial direction is applied from each cylindrical roller 4 held in each pocket 10a, 10a to the inner ring 2, The axial load acting on the inner ring 2 from the outside is offset or reduced. Since the structure and operation of the other parts are the same as the structure shown in FIG. 4 described above, the illustration and description of the equivalent parts are omitted or simplified, and the following description will focus on the characteristic parts of this embodiment.

  In the case of the present embodiment, the cage 5a is formed in a cylindrical shape from a metal plate such as a stainless steel plate. And each said pocket 10a, 10a which hold | maintains each said cylindrical roller 4 so that rolling is possible is formed in the circumferential direction several places of this holder | retainer 5a. In particular, in this embodiment, as shown in FIG. 1, the pockets 10a and 10a are inclined in predetermined directions with respect to a virtual line α parallel to the central axis of the cage 5a.

In the case of the cylindrical roller bearing with a flange according to the present embodiment, for example, the inner ring 2 is fitted and fixed to a rotating shaft having a helical gear fixed to the end, and the outer ring 3 (see FIG. 4) is fitted to the housing. By fixing, the rotating shaft is rotatably supported with respect to the housing. Therefore, during operation of the apparatus incorporating the helical gear, an axial load F _a1 as shown in FIG. 2 acts on the inner ring 2 from the rotating shaft. In FIG. 2, since the inclination angle of the cylindrical roller 4 is shown in an exaggerated manner, a gap is formed between the axial end surface of the cylindrical roller 4 and the inner side surface 13 of the outward flange 7 formed at the end of the inner ring 2. It is shown in a state of being provided. In practice, however, the inner side surface 13 and the end surface in the axial direction of the cylindrical roller 4 abut.

In the case of the present embodiment, the inclination directions of the pockets 10a and 10a are the same with respect to the circumferential direction, and are held in the pockets 10a and 10a when the outer ring 3 and the inner ring 2 are rotated relative to each other. and axial direction of the force acting above the respective cylindrical roller 4 to the inner ring 2 has a direction in which the non-opposing and the axial load F _a1. That is, the axial load F _a1 acts on the inner ring 2 from the left in FIGS. 1 and 2, and the cage 5a (not shown in FIG. 2) is located below the inner ring 2 in FIGS. In the case of relative rotation, the pockets 10a and 10a are inclined in a direction toward the lower side of the figure as it goes to the right in the figure, as shown in FIG. In this case, the inner ring 2 and the cage 5a rotate upward in FIG. However, since the cage 5a has a lower rotational speed than the inner ring 2, the cage 5a rotates relative to the inner ring 2 downward in FIG.

  It should be noted that the inclination angle θ of each of the pockets 10a and 10a depends on the pocket clearance between the outer peripheral surface of each cylindrical roller 4 and the inner peripheral surface of each of the pockets 10a and 10a, and the axial length of each cylindrical roller 4. Determined by For example, in the case of a general cylindrical roller bearing, the inclination angle θ of each of the pockets 10a and 10a is 0.6 to 1.3 ° (preferably 0.6 to 0.9 ° with respect to the virtual line α. ). In the case of this embodiment, although not shown, an arrow or the like indicating the rotational direction is imprinted on the end face of the outer ring 3 (see FIG. 4) or the inner ring 2. The place where such a mark is attached may be a place where it can be visually recognized from the outside, and the mark may be recognized if the direction of rotation or the direction of assembly is known. For example, a name number for identifying a bearing specification that is usually engraved on the end face of the outer ring 3 can be used as this mark.

  In the present embodiment, the case where the present invention is applied to the structure in which the inner ring 2 rotates is described. However, the present invention can also be applied to a structure in which the outer ring rotates and an axial load acts on the outer ring. Also in this case, each pocket of the cage is inclined so that an axial force acts on the outer ring from each cylindrical roller in a direction opposite to the axial load acting on the outer ring.

In the case of this embodiment configured as described above, since the pockets 10a and 10a are inclined, the cylindrical rollers 4 held in the pockets 10a and 10a are exaggerated in FIG. Skew occurs. For this reason, when each cylindrical roller 4 rotates relative to the inner ring 2, a force is generated from each cylindrical roller 4 toward the inner ring 2 in the axial direction. That is, in the case of the present embodiment, the cylindrical rollers 4 held in the pockets 10a and 10a of the cage 5a have a speed relative to the inner ring 2 in a direction perpendicular to the axial direction of the cylindrical rollers 4. v tends to move relatively in _r. However, since each of these cylindrical rollers 4 is restrained by the cage 5a, the cylindrical rollers 4 actually move relative to the inner ring 2 in the circumferential direction at a speed v _i . Accordingly, the axial force F _a2 acts on the inner ring 2 from the cylindrical rollers 4 due to the difference between the two velocities v _r and v _i .

In this embodiment, as described above, the inner ring 2 in which the axial load F _a1 is applied, the axial load F _a1 facing said axial force F _a2 from each cylindrical roller 4 in the direction of acts. Therefore, the axial load F _a1 acting on the inner ring 2, can be canceled or reduced by the axial force F _a2. On the other hand, between the above-mentioned cylindrical roller 4 and the outer ring 3, with respect to the outer ring 3 from the respective cylindrical rollers 4, said axial load F _a1 in the same direction axial force (right side in FIG. 2) Works.

  That is, since the cage 5a holding the cylindrical rollers 4 rotates in the same direction as the inner ring 2 (upward in FIG. 2), the retainer 5a does not rotate on the outer ring 3 that does not rotate when fitted in the housing. On the other hand, it relatively rotates upward in FIG. Therefore, in the same manner as the axial force acting between the cylindrical rollers 4 and the inner ring 2, an axial force acts on the outer ring 3 from the cylindrical rollers 4 to the right in FIG. .

Accordingly, by inclining the cylindrical rollers 4 as described above, forces in opposite directions act on the inner ring 2 and the outer ring 3 from the cylindrical rollers 4, respectively. Therefore, the axial load F _a1 acting on the flanged cylindrical roller bearing, the inner surfaces 13 of the inner ring 2 and the outward flange portion 7 and the inward flange portion 9 and 9 are formed respectively on the outer ring 3 (see FIG. 4) The force acting in the direction in which each inner side surface 13 and both end surfaces approach each other between both end surfaces in the axial direction of each cylindrical roller 4 is offset or reduced. As a result, even if the axial load Fa ₁ acting on the inner ring 2 is large, it is possible to suppress an increase in contact pressure at the contact portion between the inner side surface 13 and both end surfaces.

  In the case of this embodiment, each cylindrical roller 4 is skewed, so that the contact area at each contact portion between both end surfaces of each cylindrical roller 4 and each inner side surface of each flange 7, 9 is increased. There is a possibility that the contact pressure at each of these contact portions will increase. However, the inclination angle θ of each of the pockets 10a and 10a holding the cylindrical rollers 4 is 0.6 to 1.3 ° in a general flanged cylindrical roller bearing as described above. The inclination angle of the cylindrical roller 4 is also about 0.6 to 1.3 °. For this reason, the influence of the increase in the contact pressure at each contact portion due to the skew of each cylindrical roller 4 is small. Accordingly, the abutment portions are caused by the axial force acting on the inner ring 2 and the outer ring 3 from the cylindrical rollers 4 rather than the rate at which the contact pressure increases at the abutment portions due to the reduction of the contact area. The rate at which the contact pressure decreases is greater, and as a result, the increase in contact pressure at each of the contact portions can be suppressed. In particular, if appropriate crowning is applied to the axial end surfaces of the cylindrical rollers 4, the increase in contact pressure due to the skew can be suppressed to an extent that there is almost no problem.

  However, when the inclination angle θ of each of the pockets 10a and 10a is larger than 1.3 °, the rolling resistance of the cylindrical rollers 4 increases and the rotational resistance of the flanged cylindrical roller bearing increases. In addition, the influence of the increase in contact pressure at each contact portion due to the skew of each cylindrical roller 4 is increased, and the increase in contact pressure at each contact portion is sufficiently suppressed regardless of the crowning of the axial end surface. It may not be possible. Therefore, in a general flanged cylindrical roller bearing, the inclination angle θ of each of the pockets 10a and 10a is preferably 1.3 ° (more preferably 0.9 °) or less. On the other hand, when the inclination angle θ is smaller than 0.6 °, the axial force acting on the inner ring 2 and the outer ring 3 from the cylindrical rollers 4 is reduced. An increase in contact pressure at the contact portion cannot be sufficiently suppressed. For this reason, in a general flanged cylindrical roller bearing, the inclination angle θ is preferably 0.6 ° or more.

In this embodiment, since the outer ring 3 or the inner ring 2 is provided with a mark for identifying the rotation direction, the flanged cylindrical roller bearing can be prevented from being mistakenly assembled to the rotation support portion. The effect of this embodiment can be obtained with certainty. That is, in the case of the structure of this embodiment, the direction of the axial force acting on the inner ring 2 and the outer ring 3 from each cylindrical roller 4 is determined by the rotation direction. Therefore, it when the assembly direction is opposite, axial load F _a1 in the same direction of the force acting of the inner ring 2 from fitted the rotary shaft, acting on the inner ring 2 to 4 each cylindrical roller Thus, the contact pressure at the contact portion between the both end surfaces of each cylindrical roller 4 and the inner side surfaces 13 of the flanges 7 and 9 increases. For this reason, in the case of the structure of the present embodiment, as described above, by providing a mark that can identify the rotation direction, it is possible to prevent erroneous assembly and to reliably obtain the above-described effects. .

  FIG. 3 shows four types of flanged cylindrical roller bearings that are objects of this embodiment. Of these, (A) shows the NJ type, which is the same as the structure shown in FIG. 4, (B) shows the NUP type, (C) shows the NF type, and (D) shows the NH type. ing. In each of the structures (A) to (D), the cage is omitted. In the case of each structure shown in (A) to (D), at least the inner ring raceway 6 and the outer ring raceway 8 are axially connected to each other among the axial ends of the inner ring raceway 6 and the outer ring raceway 8. Outward and inward flanges 7, 9 provided on the opposite end, respectively, separately or separately from the outer ring 3 and the inner ring 2, with the inner side surface 13 facing the axial end surface of each cylindrical roller 4. It has. An axial load can be supported based on the engagement between the inner side surfaces 13 and 13 of the flanges 7 and 9 and the axial end surfaces of the cylindrical rollers 4. The present embodiment is applied to a structure in which such an axial load can be supported, and is an object of the invention described in the above-mentioned Patent Document 1, and N, NU, which is a structure that cannot support the axial load. NNU and NN type cylindrical roller bearings with flanges are not intended. Further, the “cylindrical roller” constituting the flanged cylindrical roller bearing of this embodiment includes a “needle”. Therefore, the above-described flanged cylindrical roller bearing includes a flanged needle bearing.

The schematic diagram which exaggerates the inclination of each pocket, and shows the holder | retainer integrated in the Example of this invention. In order to explain the effect of the present invention, a schematic diagram showing forces acting on an inner ring and a cylindrical roller during operation in an exaggerated state of the inclination of the cylindrical roller. The half part sectional view which shows four kinds of flanged cylindrical roller bearings which are the object of the present invention in a state where the cage is omitted. Sectional drawing which shows the state which incorporated the flanged cylindrical roller bearing used as the object of this invention in the rotation support part. The schematic diagram for showing the arrangement | sequence state of the pocket of the holder | retainer integrated in the conventional cylindrical roller bearing with a flange.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Cylindrical roller bearing 2 Inner ring 3 Outer ring 4 Cylindrical roller 5, 5a Cage 6 Inner ring raceway 7 Outward flange part 8 Outer ring raceway 9 Inward flange part 10, 10a Pocket 11 Rotating shaft 12 Housing 13 Inner side surface

Claims (3)

  An outer ring having a cylindrical outer ring raceway on the inner peripheral surface, an inner ring having a cylindrical inner ring raceway on the outer peripheral surface, and a plurality of cylindrical rollers provided in a freely rollable manner between the inner ring raceway and the outer ring raceway, A cage having pockets for rotatably holding these cylindrical rollers at a plurality of locations in the circumferential direction, and at least the inner ring raceway and the outer ring raceway among the axial ends of the inner ring raceway and the outer ring raceway. The end portions which are opposite to each other in the axial direction are provided with flanges which are provided integrally with or separately from the outer ring and the inner ring, and whose inner side faces the axial end surfaces of the cylindrical rollers. In the flanged cylindrical roller bearing that is capable of supporting an axial load based on the engagement between the inner surface of the cylindrical portion and the axial end surfaces of the cylindrical rollers, the pockets are parallel to the central axis of the cage. Circumferential direction for each virtual line Are inclined in the same direction, and this inclination direction is an axial force that acts on the outer ring or the inner ring from the cylindrical rollers held in the pockets when the outer ring and the inner ring rotate relative to each other. However, the flanged cylindrical roller bearing is characterized in that it is in a direction opposite to the axial load acting on the outer ring or the inner ring from the outside.   The flanged cylindrical roller bearing according to claim 1, wherein an inclination angle of each pocket is 0.6 to 1.3 ° with respect to an imaginary line parallel to the central axis of the cage.   The flanged cylindrical roller bearing according to any one of claims 1 to 2, wherein a mark capable of identifying a rotation direction is provided in part.

Images