JP2022043549A - Jump-up prevention jig for double-row self-aligning roller bearing and double-row self-aligning roller bearing - Google Patents

Abstract

To provide a jump-up prevention jig for an asymmetric double-row self-aligning roller bearing which can prevent bearing constituents from being displaced from each other during transportation or assembling, dispenses with the application of displacement-prevention processing to a raceway ring, achieves cost reduction or the like, and makes it possible to freely select a thickness of the raceway ring, and to provide the double-row self-aligning roller bearing.SOLUTION: A jump-up prevention jig 17 is used for transporting or assembling an asymmetric double-row self-aligning roller bearing 1, and prevents bearing constituents from being displaced from each other. The jump-up prevention jig 17 has: an erecting plate part 18 which abuts on an end face of an inner ring 2; a plurality of claw parts 19 protruding inward in an axial direction from an inside face of the erecting plate part 18, and constraining rollers 4 of a cage 6 between the rollers which adjoin each other in a circumferential direction; and a salient part 20 which exhibits a retention effect by contacting with a raceway surface 3a of an outer ring 3 while protruding outward in a radial direction from the claw parts 19.SELECTED DRAWING: Figure 1

Description

INDUSTRIAL APPLICABILITY The present invention relates to a double-row self-aligning roller bearing applied to applications in which an uneven load is applied to two rows of rollers arranged in the bearing width direction, for example, a bearing that supports a spindle of a wind power generator or an industrial machine. The present invention relates to a pop-out prevention jig for double-row self-aligning roller bearings and a double-row self-aligning roller bearing used for transporting or assembling.

As in the double row self-aligning roller bearing 51 shown in FIG. 10, the axial load is applied by making the lengths L1 and L2 of the two rows of rollers 54 and 55 interposed between the inner ring 52 and the outer ring 53 different from each other. It has been proposed that the load capacity of the roller 55 in the row to be received is larger than the load capacity of the roller 54 in the row to receive almost no axial load (Patent Document 1). By setting the roller lengths L1 and L2 so that the load capacity of the rollers 54 and 55 in each row becomes an appropriate size, the rolling life of the rollers 54 and 55 in each row becomes almost the same, and the bearing as a whole is substantially the same. The life can be improved.

Further, as in the double row self-aligning roller bearing 61 shown in FIG. 11, the contact angles θ1 and θ2 of the two rows of rollers 64 and 65 interposed between the inner ring 62 and the outer ring 63 are made different from each other, and the contact angle θ2 is formed. It has been proposed that the larger roller 65 can receive a large axial load and a part of the radial load, and the smaller contact angle θ1 can receive the rest of the radial load 64 (patented). Document 2). By setting the contact angles θ1 and θ2 so that the load capacity of the rollers 64 and 65 in each row becomes an appropriate size, the rolling life of the rollers 64 and 65 in each row becomes almost the same, and the actual life of the entire bearing becomes almost the same. Can be improved.

As shown in FIG. 10, the double-row self-aligning roller bearings 51 having different shapes of rollers 54 and 55 in the left and right rows, and the contact angles θ1 and θ2 of the rollers 64 and 65 in the left and right rows are different from each other as shown in FIG. In the double row self-aligning roller bearing 61, the center of gravity in the bearing width direction and the center position in the bearing width direction do not match. For this reason, the balance is poor, and when the bearing is assembled or incorporated into another device, the centering operation may be performed without permission, and care must be taken in handling. For example, as shown in FIG. 12, the inner ring 2 and the outer ring 3 are tilted with respect to the facing state, and the width surfaces 2d and 2c of the inner ring 2 protrude in the bearing width direction from the width surfaces 3b and 3c of the outer ring 3. The rollers 4 and 5 operate together with the inner ring 2. FIG. 12 shows a double-row self-aligning roller bearing in which the contact angles of the rollers 4 and 5 in the left and right rows are different from each other. do.

Therefore, as shown in FIG. 13, the applicant has provided screw holes 66, 67 on the end faces of the raceway rings in the asymmetric double-row self-aligning roller bearing, and the screw holes 66, 67 are provided from the end faces of the outer ring. Also, a pop-out prevention jig 68 that prevents the end face of the inner ring from popping out in the bearing width direction can be attached (Patent Document 3).

International Publication No. 2005/050038 Pamphlet U.S. Pat. No. 2014/0112607 Japanese Unexamined Patent Publication No. 2018-115762

In the example of FIG. 13, in order to attach the pop-out prevention jig 68, it is necessary to machine screw holes 66 and 67 on the end faces of the raceway rings. This increases the manufacturing cost. In addition, since fastening and disconnection work using bolts is required, the work man-hours become a burden. Since the screw holes 66 and 67 are machined on the end faces of the raceway ring, it may not be possible to freely select the wall thickness of the raceway ring depending on the diameter of the screw hole to be adopted.

An object of the present invention is to prevent the bearing components from shifting from each other during transportation or assembly in an asymmetric double-row self-aligning roller bearing, and to reduce the cost because it is not necessary to process the raceway ring to prevent slippage. It is an object of the present invention to provide a double-row self-aligning roller bearing and a jig for preventing pop-out thereof, in which the wall thickness of the raceway ring can be freely selected.

The pop-out prevention jig for double-row self-aligning roller bearings of the present invention conveys or assembles asymmetric double-row self-aligning roller bearings in which one or both of the two-row roller shapes and contact angles are different from each other. It is a pop-out prevention jig that is sometimes used to prevent the bearing components from shifting from each other.
A standing plate portion that is applied to the end faces of the inner ring or outer ring of the double-row self-aligning roller bearing and extends in the circumferential direction over a plurality of rollers.
A pillar portion of a cage in the double-row self-aligning roller bearing or a plurality of claw portions that restrain the rollers, which protrude inward in the axial direction from the inner surface of the standing plate portion and are adjacent to each other in the circumferential direction.
It is provided in a portion connected to the standing plate portion and extends inward in the axial direction, and protrudes radially outward or inward from the portion extending inward in the axial direction to come into contact with a part of the outer ring to obtain a retaining effect. It has a protrusion.
The bearing components are an inner ring, an outer ring, rollers and a cage.

According to this configuration, when transporting or assembling this double-row self-aligning roller bearing, the standing plate portion of the pop-out prevention jig is applied to the end face of the inner ring or the outer ring and held by a plurality of claw portions protruding from the standing plate portion. Restrain the pillars or rollers of the vessel. In the state where the pillar or roller is restrained, the protruding portion that protrudes radially outward or inward from the portion that is connected to the standing plate portion and extends inward in the axial direction comes into contact with a part of the outer ring to obtain a retaining effect. .. As a result, a frictional force acts between the pillar or roller of the cage and the plurality of claws, and a part of the outer ring is restrained by the protrusion. Therefore, bearing components such as inner and outer rings and rollers are displaced from each other. It is possible to easily and surely prevent the bearing from jumping out. When using this double-row self-aligning roller bearing, the pop-out prevention jig can be removed by the reverse procedure of the above. Since it is not necessary to machine a screw hole on the end face of the raceway ring, the manufacturing cost can be reduced and the wall thickness of the raceway ring can be freely selected.

The portion connected to the standing plate portion and extending inward in the axial direction is the plurality of claw portions, and the protruding portion may be provided on the outer peripheral surface of each of the claw portions and come into contact with the raceway surface of the outer ring. .. In this case, the protruding portion provided on the outer peripheral surface of each claw portion comes into contact with and is pressed against the raceway surface of the outer ring. Further, since a frictional force acts between the pillar or roller of the cage and the plurality of claws, the pop-out prevention jig is prevented from coming off by the frictional force and the pressing force of the protruding portion. Therefore, as a result of restraining the bearing components such as the inner and outer rings and rollers with respect to the pop-out prevention jig, it is possible to easily and surely prevent the inner and outer rings from being displaced from each other in the axial direction and the circumferential direction.

Each of the claw portions may have a proximal end side portion that becomes narrower from the proximal end side toward the distal end side and is interposed between adjacent rollers in a wedge shape. By having the base end side portions formed in a wedge shape on both side surfaces of each claw portion in this way, the portions of both side surfaces of each claw portion are firmly pushed between the rollers. Therefore, the frictional force acting between the roller and the claw portion can be increased as compared with the claw portion having a constant width. This can prevent the pop-out prevention jig from being undesirably detached.

The portion connected to the standing plate portion and extending inward in the axial direction is a partial cylindrical portion that protrudes inward in the axial direction from the outer peripheral edge of the standing plate portion and covers a part of the outer peripheral surface of the outer ring. The shape portion, the standing plate portion, and the claw portion may be formed in a groove shape in cross section. In this case, since a frictional force acts between the outer peripheral surface of the outer ring and the inner peripheral surface of the partially cylindrical portion, it is possible to more reliably prevent the displacement of the bearing components such as the inner and outer rings and the rollers.

The protruding portion may be provided at the axial tip portion of the partially cylindrical portion and may be fitted into an oil hole provided on the outer peripheral surface of the outer ring. By fitting the protrusion into the oil hole using the existing oil hole, the outer ring is securely restrained by the protrusion.

The double-row self-aligning roller bearing of the present invention includes an inner / outer ring, two rows of rollers interposed between the inner / outer rings and arranged in the bearing axial direction, and a cage for holding the rollers in each row. The raceway surface of the outer ring is spherical, the outer peripheral surface of the two rows of rollers has a cross-sectional shape along the raceway surface of the outer ring, and the two rows of rollers have one or both of the respective shapes and contact angles. The cages are different from each other in that the cage has an annular annular portion that guides the axially inner end face of the rollers of each row, and an annular portion that extends axially outward from the annular portion and is spaced at regular intervals along the circumferential direction. A multi-row self-aligning roller bearing provided with a plurality of pillars provided in the above and a pocket for holding the rollers between these pillars.
The outer ring is provided with a screw hole that penetrates in the radial direction between the rows of the two rows of rollers, and the outer peripheral surface of the annular portion of the cage has a tip portion of a male screw member screwed from the screw hole. An engageable recess is provided.

According to this configuration, when transporting or assembling this double-row self-aligning roller bearing, a male screw member is screwed into the screw hole of the outer ring, and the male screw member is inserted into the recess provided on the outer peripheral surface of the annular portion of the cage. Engage the tip. This makes it possible to stop the axial movement of the cage. Therefore, it is possible to easily and surely prevent the bearing components such as the inner and outer rings and rollers from being displaced from each other. When using this double row self-aligning roller bearing, the male screw member can be separated from the screw hole of the outer ring by the reverse procedure of the above. Since it is not necessary to machine a screw hole on the end face of the raceway ring, the manufacturing cost can be reduced and the wall thickness of the raceway ring can be freely selected.

The pop-out prevention jig for double-row self-aligning roller bearings of the present invention conveys or assembles asymmetric double-row self-aligning roller bearings in which one or both of the two-row roller shapes and contact angles are different from each other. It is a pop-out prevention jig that is sometimes used to prevent the bearing components from shifting from each other. The pillar portion of the cage or the roller in the double-row self-aligning roller bearing is restrained between the standing plate portion extending to the surface and the rollers protruding inward in the axial direction from the inner side surface of the standing plate portion and adjacent to each other in the circumferential direction. A plurality of claws to be provided, and a portion connected to the standing plate portion and extending inward in the axial direction, and protruding inward or outward in the radial direction from the portion extending inward in the axial direction to form a part of the outer ring. It has a protruding portion that comes into contact and obtains a retaining effect. For this reason, in asymmetric double-row self-aligning roller bearings, it is possible to prevent the bearing components from shifting from each other during transportation or assembly, and it is not necessary to process the raceway wheels to prevent slippage, resulting in cost reduction. , The wall thickness of the bearing ring can be freely selected.

The double-row self-aligning roller bearing of the present invention includes inner and outer rings, two rows of rollers interposed between the inner and outer rings and aligned in the bearing axial direction, and a cage for holding the rollers in each row. The raceway surface of the outer ring is spherical, the outer peripheral surface of the two rows of rollers has a cross-sectional shape along the raceway surface of the outer ring, and the two rows of rollers have one or both of the respective shapes and contact angles. Are different from each other, and the cage has an annular ring portion that guides the end face of the roller on the inner side in the axial direction of each row, and an annular portion that extends outward in the axial direction from the annular portion and is spaced at regular intervals along the circumferential direction. This is a double-row self-aligning roller bearing provided with a plurality of pillars provided in the above, and a pocket for holding the rollers is provided between the pillars. A screw hole penetrating in the radial direction is provided, and a recess portion that can be engaged with the tip end portion of the male screw member screwed from the screw hole is provided on the outer peripheral surface of the annular portion of the cage. For this reason, in asymmetric double-row self-aligning roller bearings, it is possible to prevent the bearing components from shifting from each other during transportation or assembly, and it is not necessary to process the raceway wheels to prevent slippage, resulting in cost reduction. , The wall thickness of the bearing ring can be freely selected.

It is sectional drawing of the double row self-aligning roller bearing which concerns on 1st Embodiment of this invention, and the pop-out prevention jig. It is a top view of the pop-out prevention jig and a bearing component. It is an enlarged cross-sectional view which partially enlarged the protruding part of the pop-out prevention jig. It is sectional drawing of the pop-out prevention jig of the double row self-aligning roller bearing which concerns on other embodiment of this invention. It is a side view of the pop-out prevention jig and the like. It is sectional drawing of the double row self-aligning roller bearing which concerns on still another Embodiment of this invention, and the pop-out prevention jig. It is an enlarged cross-sectional view which saw a part of the pop-out prevention jig and a cage partially enlarged. It is a perspective view which cut out and represented a part of an example of the spindle support device of a wind power generation device. It is a breaking side view of the main shaft support device. It is sectional drawing of the double row self-aligning roller bearing of the 1st proposal example. It is sectional drawing of the double row self-aligning roller bearing of the 2nd proposal example. It is sectional drawing which shows the state which the inner ring and the outer ring of a multi-row self-aligning roller bearing are inclined to each other with respect to the state which faces each other. It is sectional drawing of the multi-row self-aligning roller bearing of the conventional example, and the pop-out prevention jig thereof.

[First Embodiment]
An embodiment of the present invention will be described with reference to FIGS. 1 to 3.
The pop-out prevention jig for double-row self-aligning roller bearings of this embodiment is used when transporting or assembling an asymmetric double-row self-aligning roller bearing to prevent the bearing components from shifting from each other.

<About double row self-aligning roller bearings>
As shown in FIG. 1, the double-row self-aligning roller bearing 1 has inner and outer rings 2 and 3, rollers 4 and 5 in two rows on the left and right, and rollers 4 and 5 in each row. 7 and. When this double row self-aligning roller bearing 1 is used under conditions where an axial load and a radial load act, it is used.
A roller 5 in the right column having a large contact angle, which will be described later, bears almost all of the axial load and a part of the radial load, and a roller 4 in the left column having a small contact angle bears the rest of the radial load.

The rollers 4 and 5 in the left and right rows are arranged in the bearing axial direction between the inner ring 2 and the outer ring 3. The raceway surface 3a of the outer ring 3 has a spherical shape, and the outer peripheral surfaces of the rollers 4 and 5 in the left and right rows have a cross-sectional shape along the raceway surface 3a of the outer ring 3. In other words, the outer peripheral surfaces of the rollers 4 and 5 are rotating curved surfaces obtained by rotating an arc along the raceway surface 3a of the outer ring 3 around the center lines C1 and C2. The inner ring 2 is formed with double-row raceway surfaces 2a and 2b having a cross-sectional shape along the outer peripheral surfaces of the rollers 4 and 5 in the left and right rows.

As shown in FIGS. 1 and 2, the cage 6 for the left column has an annular annular portion 32 that guides the end face of the roller 4 in the left column in the axial direction, and an annular portion 32 that is axially outward from the annular portion 32. It is provided with a plurality of pillar portions 33 which extend to and are provided at intervals determined along the circumferential direction. A pocket Pt for holding the roller 4 is provided between these pillars. The outer peripheral surface and the inner peripheral surface of each pillar portion 33 are provided parallel to the bearing axis direction.

As shown in FIG. 1, the cage 7 for the right column holds the rollers 5 in the right column that receive an axial load. The cage 7 has an annular ring portion 34 that guides the end surface of the roller 5 in the right column on the inner side in the axial direction, and an interval that extends outward in the axial direction from the annular portion 34 and is determined along the circumferential direction. It is provided with a plurality of pillar portions 35 provided in a standing position. The outer diameter surface of the pillar portion 35 has an inclination angle β that inclines inward in the radial direction from the proximal end side toward the distal end side. This inclination angle β is an angle with respect to the bearing central axis O. The inclination angle β is larger than zero and is set in the range (0 <β ≦ α2) of the maximum diameter angle α2 or less of the roller 5. The maximum diameter angle α2 is an inclination angle at a position where the maximum diameter D2 _max of the roller 5 in the right column is obtained with respect to a plane perpendicular to the bearing center axis O.

The inner diameter surface of the pillar portion 35 has an inclination angle γ that inclines inward in the radial direction from the proximal end side toward the distal end side. This tilt angle γ is also an angle with respect to the bearing central axis O, and the tilt angle γ is set so as to be equal to or greater than the tilt angle β (γ ≧ β). However, the relationship is not limited to this relationship (γ ≧ β). In this example, the tilt angle γ is set to the same angle as the tilt angle β.

Since the cage 7 for the right column has the inclination angle β as described above, the pocket surface of the cage 7 can hold the maximum diameter position of the roller 5. As a result, the posture stability of the rollers 5 in the row receiving the axial load is not impaired, and the rollers 5 can be easily incorporated.

A brim (small brim) 8 and 9 are provided at both ends of the outer peripheral surface of the inner ring 2, respectively. A middle brim 10 is provided at the center of the outer peripheral surface of the inner ring 2, that is, between the rollers 5 in the right column and the rollers 4 in the left column. The inner ring 2 may have no brim. The outer ring 3 has an annular oil groove 11 between the left and right roller rows on the outer peripheral surface, and the oil hole 12 which is a screw hole penetrating from the oil groove 11 to the inner peripheral surface is one or more in the circumferential direction. It is provided in a place.

The rollers 4 and 5 in each of the left and right rows have the same length along the center lines C1 and C2, the maximum diameters D1 _max and D2 _max are also the same, and the rollers 4 and 5 in each of the left and right rows have the same length. Is also said to be asymmetrical. The asymmetric roller is a roller having an asymmetric shape in which the positions of the maximum diameters D1 _max and D2 _max are deviated from the center of the roller length. In the example of FIG. 1, the position of the maximum diameter D1 _max of the roller 4 in the left column is to the right of the center of the roller length, and the position of the maximum diameter D2 _max of the roller 5 in the right column is from the center of the roller length. It's on the left.

Further, the contact angle θ2 of the roller 5 in the right column is set larger than the contact angle θ1 of the roller 4 in the left column. By making the rollers 4 and 5 in the left and right rows the above-mentioned asymmetric rollers, the positions of the rollers 4 and 5 are not changed with respect to the symmetrical rollers (not shown) whose maximum diameter is in the center of the roller length. In addition, the contact angles θ1 and θ2 can be changed. The optimum contact angle can be set by adjusting the distance from the center of the roller length to the position of the maximum diameter. In the example of FIG. 1, the distance is set larger in the roller 5 in the right column than in the roller 4 in the left column.

The action lines S1 and S2 forming the contact angles θ1 and θ2 of the rollers 4 and 5 in each row intersect each other at the center of alignment P on the bearing center axis O. As a result, the inner ring 2 and the rollers 4 and 5 can be aligned along the raceway surface 3a of the outer ring 3. The bearing axial position of the centering point P is shifted to the side of the roller 4 where the contact angle θ1 is smaller than the center position Q of the center brim 10 in the bearing axial direction. The action lines S1 and S2 are lines on which the combined force of the forces acting on the contact portions between the rollers 4 and 5 and the inner ring 2 and the outer ring 3 acts.

Crowning may be provided on the rolling surface of any one or both of the rollers 4 and 5 in each row. By providing crowning, the diameter of curvature at both ends is made smaller than that at the center of the rolling surface. The shape of the crowning is, for example, a logarithmic curve. In addition to the logarithmic curve, the shape may be a straight line, a single arc, or a combination of a plurality of arcs. By providing crowning at both ends of the rolling surfaces of the rollers 4 and 5 in this way, the surface pressure at both ends where the sliding speed is large on the rolling surfaces of the rollers 4 and 5 is reduced, and the PV value (surface pressure x sliding speed). The absolute value of is suppressed, and friction can be reduced. In particular, it is preferable to provide crowning at the roller 5 in the right column of FIG. 1 which receives an axial load.

As described above, in the double-row self-aligning roller bearing 1 shown in FIG. 1, since the contact angles θ1 and θ2 of the rollers 4 and 5 in the left and right rows are different from each other, the center of gravity in the bearing axial direction and the center position in the bearing axial direction are located. It doesn't match Q and the balance is bad. Therefore, there is a possibility that the double-row self-aligning roller bearing 1 may undesirably perform an alignment operation during transportation or assembly, that is, the bearing components may be displaced from each other. The time of assembling includes the time of assembling the double row self-aligning roller bearing 1 into another device. Therefore, a pop-out prevention jig 17 is provided to prevent the bearing components from shifting from each other during transportation or assembly of the double-row self-aligning roller bearing 1.

<About the pop-out prevention jig 17>
As shown in FIGS. 1 and 2, the pop-out prevention jig 17 has a standing plate portion 18, a plurality of claw portions 19, and a protruding portion 20. The standing plate portion 18, the claw portion 19, and the protruding portion 20 are integrally formed of, for example, a synthetic resin or the like. The "integrally formed" means that the standing plate portion 18, the plurality of claw portions 19, and the protruding portions 20 are not formed by combining a plurality of elements, but are made of a single material, for example, by injection molding or machining. It means that it was molded as a part or as a whole of a single object.

The standing plate portion 18 has a standing plate shape that is applied to the end surface of the inner ring 2 on the left column side and extends outward in the radial direction, and has a circumferential circumference over a plurality of rollers (three in this example) arranged in the circumferential direction. Extend in the direction. The plurality of (two in this example) claw portions 19 are portions connected to the standing plate portion 18 and extending inward in the axial direction, and project inward in the axial direction from the outer diameter side portion on the inner surface of the standing plate portion 18. .. Each claw portion 19 becomes narrower from the proximal end side toward the distal end side and is interposed between the adjacent rollers 4 and 4 in a wedge shape, and the proximal end side portion 19a connected to the proximal end side portion 19a. And have.

For example, the proximal end side portion 19a is formed from the proximal end side to the portion having the maximum diameter position of the roller 4, and the distal end side portion 19b becomes wider toward the distal end side from the portion having the maximum diameter position and extends to the distal end. .. Further, in this example, the plurality of claw portions 19 press the outer peripheral surface of the pillar portion 33 of the cage 6 between the rollers adjacent to each other in the circumferential direction. The length of the claw portion 19 is set to be a length extending beyond the maximum diameter position of the roller 4. The claw portion 19 of this example extends from the pillar portion 33 of the cage 6 to a part of the outer peripheral surface of the annular portion 32. The claw portion 19 may extend to the vicinity of the base end of the pillar portion 33 and may not extend to the annular portion 32. The claw portion 19 and the standing plate portion 18 are formed into an L-shaped cross section when the claw portion 19 and the standing plate portion 18 are cut along a plane including the bearing axial direction.

As shown in FIGS. 2 and 3, the protruding portion 20 projects radially outward from the proximal end side portion of the outer peripheral surface of each claw portion 19 and comes into contact with the raceway surface 3a of the outer ring 3. The protruding portion 20 extends in the circumferential direction on the outer peripheral surface of each claw portion 19. Each protruding portion 20 has a spherical convex cross section, and the tip portion on the outer diameter side of the convex shape is set to be larger than the inner diameter D3 of the outer ring. With the pop-out prevention jig 17 mounted on the double-row self-aligning roller bearing 1, each protrusion 20 is located axially inward from the chamfer on one end side in the axial direction of the roller 4, that is, on the left side.

<Action effect>
At the time of transporting or assembling the double-row self-aligning roller bearing 1, the standing plate portion 18 of the pop-out prevention jig 17 is applied to the end face of the inner ring 2, and the rollers 4 are formed by the plurality of claw portions 19 protruding from the standing plate portion 18. Restrain. In the state where the 4 is restrained at this time, the protruding portion 20 protruding in the radial direction from each pillar portion 33 comes into contact with the raceway surface 3a of the outer ring 3 to obtain a retaining effect. As a result, a frictional force acts between the outer peripheral surface of the roller 4 and the plurality of claw portions 19, and the inner peripheral surface of the outer ring 3 is restrained by the pressing force of the protruding portion 20.

Therefore, the bearing components such as the inner and outer rings 2 and 3 are displaced from each other, for example, the subassembly including the inner ring 2, the rollers 4 and 5 and the cages 6 and 7 is relatively tilted with respect to the outer ring 3. It is possible to easily and surely prevent the inner ring end surface from protruding in the axial direction from the outer ring end surface. When the double row self-aligning roller bearing 1 is used, the pop-out prevention jig 17 can be detached by the reverse procedure of the above. Since it is not necessary to machine a screw hole on the end face of the raceway ring, the manufacturing cost can be reduced and the wall thickness of the raceway ring can be freely selected.
By having the base end side portions 19a formed on both side surfaces of each claw portion 19 in a wedge shape, the portions of both side surfaces of each claw portion 19 are firmly pushed between the rollers 4 and 4. Therefore, the frictional force acting between the roller 4 and the claw portion 19 can be increased as compared with the claw portion having a constant width. This can prevent the pop-out prevention jig 17 from being undesirably detached. Since the pop-out prevention jig 17 is made of resin without using metal, it is possible to prevent scratches and fretting on the contact surface. Further, since the pop-out prevention jig 17 is made of resin, the mass can be reduced as compared with the metal pop-out prevention jig.

<About other embodiments>
In the following description, the same reference numerals will be given to the parts corresponding to the matters described in advance in each embodiment, and duplicate description will be omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described above unless otherwise specified. It has the same action and effect from the same configuration. Not only the combinations of the parts specifically described in each embodiment, but also the combinations of the embodiments can be partially combined as long as the combination does not cause any trouble.

[Second Embodiment]
As shown in FIGS. 4 and 5, each claw portion 19 is pushed so as to come into contact with the outer peripheral surface of the pillar portion 33 between the rollers 4 and 4, and is radially from the partial cylindrical shape portion 36 connected to the standing plate portion 18. The protruding portion 20A protruding inward may be fitted into the oil hole 12.
The pop-out prevention jig 17A includes a standing plate portion 18 that is applied to the end surface of the outer ring 3, and a plurality of claw portions 19 that project inward in the axial direction from the inner diameter side portion on the inner surface of the standing plate portion 18. A partial cylindrical portion 36 that protrudes inward in the axial direction from the outer peripheral edge of the plate portion 18 and covers a part (left column side) of the outer peripheral surface of the outer ring 3, and a radial tip portion of this partial cylindrical shape portion 36. It has a protruding portion 20A protruding inward. The partially cylindrical portion 36, the standing plate portion 18, and the claw portion 19 are formed in a groove shape in cross section.

According to this configuration, a frictional force acts between the outer peripheral surface of the outer ring 3 and the inner peripheral surface of the partially cylindrical portion 36, so that the displacement of the bearing component can be prevented more reliably. The protruding portion 20A is provided at the axial tip portion of the partial cylindrical shape portion 36, and is fitted into an oil hole 12 provided on the outer peripheral surface of the outer ring 3. Specifically, the inner peripheral surface of the partially cylindrical portion 36 can be slid inward in the axial direction to fit the protruding portion 20A into the oil hole 12. By fitting the protrusion 20A into the oil hole 12 using the existing oil hole 12, the outer ring 3 is reliably restrained by the protrusion 20A.

The protruding portion 20A is fitted into the oil hole 12 provided on the outer peripheral surface of the outer ring 3 in a state where the outer peripheral surface of the pillar portion 33 is pressed by the plurality of claw portions 19. As a result, a frictional force acts between the outer peripheral surface of the pillar portion 33 of the cage 6 and the plurality of claw portions 19, and the frictional force acts between the outer peripheral surface of the outer ring 3 and the inner peripheral surface of the partial cylindrical portion 36. And the outer ring 3 is constrained by the protrusion 20A. Therefore, the bearing components such as the inner and outer rings 2 and 3 are displaced from each other, for example, the subassembly including the inner ring 2, the rollers 4 and 5 and the cages 6 and 7 is relatively tilted with respect to the outer ring 3. It is possible to easily and surely prevent the inner ring end surface from protruding in the axial direction from the outer ring end surface. Other than that, it has the same effect as that of the above-described embodiment.

[Third Embodiment]
As shown in FIGS. 6 and 7, in the double row self-aligning roller bearing 1A according to the embodiment of the present invention, the bearings 6 and 7 are screwed into the outer peripheral surface of the annular portion from the oil hole 12 which is a screw hole. A recess 38 that can be engaged is provided at the tip of the male screw member 37. The recessed portion 38 has a hemispherical shape to which the tip portion 37a of the male screw member 37 can be engaged, and is formed in a hemispherical shape jointly by the left and right annular portions 32 and 34 that are in contact with each other in the axial direction. As the male screw member 37, for example, a spring plunger is applied. In this example, the spring plunger fixes the cages 6 and 7 to the outer ring 3, a plunger body on which a male screw portion is formed, a compression coil spring built in the plunger body, and the plan. It has a center pin that is supported by the tip of the jar body and receives the pressing force of the compression coil spring. By applying a load to this center pin, the center pin retracts into the inside of the plunger body, and when the load is released, it returns to the desired position by the pressing force of the compression coil spring. The center pin at the tip of the spring plunger is inserted into the bearing through the oil hole 12 and engaged with the recess 38 to apply a constant pressing force to the cages 6 and 7. This makes it possible to stop the axial movement of the cages 6 and 7.

Therefore, similarly to each of the above-described embodiments, it is possible to easily and surely prevent the bearing components such as the inner and outer rings 2 and 3 from being displaced from each other. When the double row self-aligning roller bearing 1A is used, the male screw member 37 can be separated from the screw hole of the outer ring 3 by the reverse procedure of the above. Since it is not necessary to machine a screw hole on the end face of the raceway ring, the manufacturing cost can be reduced and the wall thickness of the raceway ring can be freely selected. As the male screw member 37, for example, a set screw with a hexagon socket can be applied.

<Usage example of double row self-aligning roller bearings 1, 1A>
8 and 9 show an example of a spindle support device of a wind power generation device.
When transporting or assembling the double-row self-aligning roller bearings 1, 1A to this wind power generation device, the pop-out prevention jig according to any one of the embodiments is used. After assembling the multi-row self-aligning roller bearings 1, 1A, the pop-out prevention jig can be detached and reused.

The casing 23a of the nacelle 23 is horizontally swivelly installed on the support base 21 via the swivel seat bearing 22 (FIG. 9). In the casing 23a of the nacelle 23, the spindle 26 is rotatably installed via the spindle support bearing 25 installed in the bearing housing 24, and the blade 27 serving as a swivel blade is located in a portion of the spindle 26 protruding outside the casing 23a. Is attached. The other end of the spindle 26 is connected to the speed increaser 28, and the output shaft of the speed increaser 28 is coupled to the rotor shaft of the generator 29. The nacelle 23 is swiveled at an arbitrary angle by the swivel motor 30 via the speed reducer 31.

Although two spindle support bearings 25 are installed side by side in the illustrated example, one spindle support bearing 25 may be used. As the spindle support bearing 25, the double row self-aligning roller bearings 1, 1A of any of the above embodiments are used. In that case, since both the radial load and the axial load are applied to the row farther from the blade 27, the roller 5 having the larger contact angle θ2 is used as the roller in the row farther from the blade 27. Since only the radial load is mainly applied to the row closer to the blade 27, the roller 4 having the smaller contact angle θ1 is used as the roller in the row closer to the blade 27.

The pop-out prevention jigs 17 and 17A can also be formed by a 3D printer or machining.

Although the embodiments for carrying out the present invention have been described above based on the embodiments, the embodiments disclosed this time are exemplary in all respects and are not limiting. The scope of the present invention is shown by the scope of claims rather than the above description, and is intended to include all modifications within the meaning and scope equivalent to the scope of claims.

1,1A ... Double row self-aligning roller bearing, 2 ... Inner ring, 3 ... Outer ring, 3a ... Race plane, 4,5 ... Roller, 6,7 ... Cage, 12 ... Oil hole (screw hole), 17,17A ... Pop-out prevention jig, 18 ... Stand plate part, 19 ... Claw part, 19a ... Base end side part, 20, 20A ... Protruding part, 36 ... Partial cylindrical shape part, 37 ... Male screw member, 38 ... Recessed part

Claims (6)

Used when transporting or assembling asymmetric double-row self-aligning roller bearings in which one or both of the two-row roller shapes and contact angles differ from each other to prevent the bearing components from shifting from each other. It ’s a jig,
A standing plate portion that is applied to the end faces of the inner ring or outer ring of the double-row self-aligning roller bearing and extends in the circumferential direction over a plurality of rollers.
A pillar portion of a cage in the double-row self-aligning roller bearing or a plurality of claw portions that restrain the rollers, which protrude inward in the axial direction from the inner surface of the standing plate portion and are adjacent to each other in the circumferential direction.
It is provided in a portion connected to the standing plate portion and extends inward in the axial direction, and protrudes radially outward or inward from the portion extending inward in the axial direction to come into contact with a part of the outer ring to obtain a retaining effect. A jig to prevent popping out of a multi-row self-aligning roller bearing with a protrusion. In the pop-out prevention jig for the double-row self-aligning roller bearing according to claim 1, the portions connected to the standing plate portion and extending inward in the axial direction are the plurality of claw portions, and the protruding portions are the above-mentioned respective claw portions. A jig for preventing popping out of a double-row self-aligning roller bearing provided on the outer peripheral surface of the claw portion and in contact with the raceway surface of the outer ring. In the pop-out prevention jig for the double-row self-aligning roller bearing according to claim 2, each of the claws is narrowed from the proximal end side toward the distal end side and is interposed between adjacent rollers in a wedge shape. A jig to prevent popping out of double row self-aligning roller bearings with end sides. In the pop-out prevention jig for the double-row self-aligning roller bearing according to claim 1, the portion connected to the standing plate portion and extending inward in the axial direction protrudes inward in the axial direction from the outer peripheral edge of the standing plate portion. , A partially cylindrical portion that covers a part of the outer peripheral surface of the outer ring, and is a double-row self-aligning roller bearing formed in a cross-sectional groove shape by the partial cylindrical portion, the standing plate portion, and the claw portion. Pop-out prevention jig. In the pop-out prevention jig for the double row self-aligning roller bearing according to claim 4, the protruding portion is provided at the axial tip portion of the partially cylindrical portion and is provided on the outer peripheral surface of the outer ring. A jig to prevent popping out of double-row self-aligning roller bearings that are fitted into oil holes. The outer ring is provided with two rows of rollers interposed between the inner and outer rings and arranged in the bearing axial direction, and a cage for holding the rollers in each row, and the raceway surface of the outer ring is spherical. The outer peripheral surface of the rollers in the row has a cross-sectional shape along the raceway surface of the outer ring, the rollers in the two rows have different shapes and contact angles, or both, and the cage is in each row. It is provided with an annular ring portion that guides the end face on the inner side in the axial direction of the roller, and a plurality of pillar portions that extend outward from the annular portion in the axial direction and are provided at regular intervals along the circumferential direction. A multi-row self-aligning roller bearing provided with a pocket for holding the rollers between these columns.
The outer ring is provided with a screw hole that penetrates in the radial direction between the two rows of rollers, and the outer peripheral surface of the annular portion of the cage is formed on the tip of a male screw member screwed from the screw hole. Double row self-aligning roller bearings with engageable recesses.

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