Tapered roller bearing
The tapered roller bearing design addresses lubricity and size limitations by using a retainer segment with arc-shaped portions and columns, eliminating small-diameter side protrusions and enhancing lubricity and assembly stability.
Patent Information
- Application Number
- JP2023179094
- Authority / Receiving Office
- JP · JP
- Patent Type
- Applications
- Current Assignee / Owner
- Filing Date
- 2023-10-17
- Publication Date
- 2025-04-30
AI Technical Summary
Large tapered roller bearings used in wind power generation devices and industrial machinery face challenges in maintaining lubricity due to large-diameter side protrusions, which also limit bearing size and increase lubricant exposure.
The tapered roller bearing features a retainer segment with large-diameter and small-diameter arc-shaped portions connected by columns, forming pockets for tapered rollers. The small-diameter side arc portion serves as a jig engagement surface, eliminating the need for small-diameter side protrusions, thus preventing dislocation and maintaining lubricity without size limitations.
This configuration enhances lubricity by reducing lubricant exposure and prevents undesirable dislocation during assembly, allowing for larger bearing sizes without compromising performance.
Smart Images
Figure 2025068956000001_ABST
Abstract
Description
[Technical field]
[0001] The present invention relates to a tapered roller bearing for use as the main bearing of a wind turbine generator or a tapered roller bearing for use in industrial machinery, and in particular to a large tapered roller bearing having an outside diameter exceeding 1 m. [Background technology]
[0002] In rolling bearings, the cage that holds the rolling elements is usually composed of a single annular part. Metallic pressed cages, machined cages, welded cages, plastic cages, etc. are used as the cage depending on the application and characteristics. The rolling bearings that support the main shaft of a wind turbine generator are large because they bear heavy loads, making the production and assembly of the components difficult. In order to facilitate the production and assembly of the cage for such large rolling bearings, plastic cage segments that make the cage separable have been proposed (Patent Documents 1 and 2).
[0003] However, in the assembly process of single-row tapered roller bearings for wind turbine main bearings, when handling the inner ring assembly, which is made up of the inner ring, rollers, and cage, there is a procedure in which it is handled in an inverted state with the inner ring small end face facing down.In this case, in order to prevent the cage and rollers from coming apart, as shown in Figures 17 and 18, a cage segment 200 has been proposed that can be tied with a wire or the like (not shown) and handled as a single unit, and that the wire can be removed after assembly into the bearing (Patent Documents 3 and 4). [Prior art documents] [Patent documents]
[0004] [Patent Document 1] European Patent No. 1408248 [Patent Document 2] JP 2009-52476 A [Patent Document 3] JP 2022-179448 A [Patent Document 4] JP 2022-179449 A Summary of the Invention [Problem to be solved by the invention]
[0005] The cage segment 200 in Patent Documents 3 and 4 has a plurality of large diameter side protrusions 26 that engage with a wire and a jig to integrate the inner ring assembly. Since the retainer segment 200 has a small diameter side protrusion 28 in addition to the large diameter side protrusion 26, the amount of protrusion of the retainer from the bearing width face is large, and the bearing size is limited to prevent interference between the retainer and the surrounding bearing structure. Furthermore, due to the large diameter side protrusion 26 and the small diameter side protrusion 28, the amount of lubricant scraped out by the cage when the bearing rotates increases, which raises concerns about a decrease in the lubrication of the bearing.
[0006] An object of the present invention is to provide a tapered roller bearing that can improve the lubrication of the bearing without limiting the bearing size. [Means for solving the problem]
[0007] The tapered roller bearing of the present invention comprises an inner ring, an outer ring, a plurality of tapered rollers interposed between the inner ring and the outer ring, and a retainer for retaining the tapered rollers, the retainer having a plurality of retainer segments divided in the circumferential direction, the retainer segments being connected by detachable connecting members, the retainer segment has a large diameter side arcuate portion and a small diameter side arcuate portion extending in a circumferential direction, and a plurality of column portions connecting the large diameter side and small diameter side arcuate portions, the large diameter side arcuate portion, the small diameter side arcuate portion and the column portions forming pockets for accommodating a plurality of the tapered rollers, A tapered roller bearing including a protrusion having an engagement portion with the connecting member on a large diameter side surface of the large diameter side arcuate portion, The outer diameter surface of the small diameter side arcuate portion also serves as a jig engagement surface that engages with an annular jig.
[0008] According to this configuration, the large diameter side arc-shaped portions of the plurality of retainer segments are connected by the detachable connecting member. The annular jig prevents the small diameter side of the retainer segments from expanding when the connecting member is attached. In the conventional structure, in order to provide the cage segments with a surface that engages with the annular jig, a small diameter side protrusion is provided on the small diameter side surface of the small diameter side arcuate portion. In contrast, in the present configuration, the outer diameter surface of the small diameter side arcuate portion of the cage segment also serves as a jig engagement surface that engages with the annular jig, which makes it possible to prevent the cage rollers from undesirably coming apart when the inner ring assembly is reversed, without providing a small diameter side protrusion. Therefore, there is no restriction on the bearing size, and the amount of lubricant scooped out by the cage when the tapered roller bearing rotates can be reduced compared to conventional structures.
[0009] Both ends of the connecting member may be connected by a fastening portion or a fastening member, in which case the connecting member is easy to handle.
[0010] The connecting member may be divided into a plurality of pieces, and the ends of the connecting members may be connected by fastening portions or fastening members. In this case, the fastening force can be applied uniformly to the entire connecting member by the fastening portions or fastening members.
[0011] The annular jig may be attached to the small diameter side surface of the inner ring. In this case, if the annular jig is detachable from the inner ring, assembly of the bearing can be simplified.
[0012] The cage segments may be made of polyetheretherketone blended with carbon fiber or polyetheretherketone blended with glass fiber. Carbon fiber or glass fiber is fibrous, and therefore can efficiently reduce the thermal expansion coefficient. Therefore, it is possible to prevent the circumferential gap between the cage segments from becoming zero when the cage segments expand.
[0013] With tapered rollers arranged on the raceway surface of the inner ring with the large end face of the inner ring facing down, the angle at which the large rib portion of the inner ring intersects with the central axis of the inner ring at a right angle is I, the chamfer width of the tip of the large rib portion is H, the distance from the central axis of the inner ring to the center of gravity of the tapered roller is y1, and the diameter of the large rib portion is J, the following condition may be satisfied. (J / 2)-H·cosI>y1 According to this configuration, when the tapered rollers are assembled into the inner ring, the tapered rollers can be prevented from falling off due to their own weight.
[0014] In a state in which the retainer segments are connected by the connecting member, the diameter of the small rib portion of the inner ring is M, the angle that the small rib portion makes with a line perpendicular to the central axis of the inner ring is L, the chamfer width of the tip of the small rib portion is K, and when the tapered roller is rotated around the tip of the large rib portion of the inner ring, the distance from contact point C at which the side of the small rib portion and the small diameter side end face of the tapered roller come into contact with each other, to the central axis is y3, the following condition may be satisfied. (M / 2)-K·cosL>y3 According to this configuration, the small diameter end face of the tapered roller comes into contact with the contact point C on the side face of the small rib portion, so that rotation of the tapered roller about the large rib portion is suppressed.
[0015] The tapered roller bearing may be a large bearing with an outer diameter of 1 m or more used in a wind power generation device. In this case, a tapered roller bearing with no bearing size restrictions and excellent lubricity can be applied to the large bearing used in the wind power generation device, and the maintenance costs of the tapered roller bearing can be reduced. Effect of the Invention
[0016] In the tapered roller bearing of the present invention, the outer diameter surface of the small diameter side arcuate portion of the cage segment also serves as a jig engagement surface that engages with the annular jig, thereby improving the lubrication of the bearing without limiting the bearing size. [Brief description of the drawings]
[0017] [Figure 1]1 is a vertical sectional view of a tapered roller bearing according to a first embodiment of the present invention. [Diagram 2] FIG. 2 is a front view of the inner ring assembly of the tapered roller bearing as viewed from the axial direction. [Diagram 3] FIG. [Figure 4] 4 is a cross-sectional view showing a retainer segment of the retainer of the tapered roller bearing. FIG. [Diagram 5] FIG. 4 is a plan view of the retainer segment as viewed from the radial outside. [Figure 6] FIG. 2 is a perspective view showing the retainer segment. [Figure 7] FIG. 4 is a cross-sectional view of an inner ring assembly with an annular jig attached. [Figure 8] FIG. 4 is a schematic diagram showing the relationship between the tapered rollers and a large rib portion of the inner ring when the tapered rollers are arranged on the inner ring with the large end face of the inner ring facing down. [Figure 9] FIG. 4 is a perspective view showing the cage segments arranged in an annular shape. [Figure 10] 13 is a perspective view showing a state in which an annular jig and a connecting member are attached to the inner ring assembly. FIG. [Figure 11] FIG. 4 is a schematic diagram showing the rotating state of tapered rollers arranged on the raceway surface of the inner ring. [Figure 12] 4 is a schematic diagram showing the relationship between the height of a small rib portion of the inner ring and the tapered roller when the tapered roller arranged on the raceway surface of the inner ring is rotated. FIG. [Figure 13] FIG. 6 is a perspective view showing a cage segment of a tapered roller bearing according to a second embodiment of the present invention. [Figure 14] FIG. 11 is a perspective view showing an inner ring assembly of a tapered roller bearing according to a third embodiment of the present invention. [Figure 15] 2 is a perspective cross-sectional view showing a retainer segment of the retainer of the tapered roller bearing. FIG. [Figure 16] 1 is a cutaway perspective view of a wind turbine generator using a tapered roller bearing according to any one of the embodiments of the present invention. FIG. [Figure 17] FIG. 13 is a perspective view of a retainer segment according to a conventional example. [Figure 18]FIG. 13 is a perspective view of a retainer segment of another conventional example. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0018] [First embodiment] A tapered roller bearing according to an embodiment of the present invention will be described with reference to Fig. 1 to Fig. 12. This tapered roller bearing is applied, for example, to a main shaft of a wind power generating device or to a large tapered roller bearing for industrial machinery, particularly one with an outer diameter exceeding 1 m. However, the applications of the tapered roller bearing are not limited to this.
[0019] <Outline of tapered roller bearing structure> 1, the tapered roller bearing 1 of this embodiment comprises an inner ring 11, an outer ring 12, a number of tapered rollers 15 interposed between the inner and outer rings 11, 12, and a cage 17 that holds the tapered rollers 15 at regular intervals. The cage 17 has pockets 16 that open in the radial direction, and the tapered rollers 15 are held in these pockets 16.
[0020] In this specification, a tapered roller bearing may simply be referred to as a "bearing." In the following description, the direction of the bearing center axis AX is referred to as the "axial direction," the direction perpendicular to the bearing center axis AX is referred to as the "radial direction," and the circumferential direction around the bearing center axis AX is referred to as the "circumferential direction." Additionally, the side toward the bearing center axis AX is referred to as the "inner diameter side," and the side away from the bearing center axis AX is referred to as the "outer diameter side." Furthermore, the direction in the axial direction in which the diameter of the raceway surface 14 of the outer ring 12 becomes smaller is referred to as the "small diameter side," and the direction in which the diameter of the raceway surface 14 becomes larger is referred to as the "large diameter side."
[0021] The outer ring 12 has, on its inner circumference, a raceway surface 14 along which the tapered rollers 15 roll. The inner ring 11 has, on its outer circumference, a raceway surface 13 along which the tapered rollers 15 roll, and a large rib portion 19 and a small rib portion 18 on either side of the raceway surface 13 in the axial direction with which the end faces of the tapered rollers 15 come into contact.
[0022] <Regarding cage segments, etc.> FIG. 2 is a front view of an inner ring assembly As including an inner ring 11, a cage 17, and tapered rollers 15, as viewed from the axial direction. The cage 17 is a segment cage having a plurality of cage segments 20 divided in the circumferential direction. In detail, the plurality of cage segments 20 are connected by connecting members 25 (FIG. 1) described below to form the cage 17. The cage segments 20 in this embodiment are made of resin. In detail, the cage segments 20 are made of, for example, polyetheretherketone blended with carbon fiber or polyetheretherketone blended with glass fiber. However, the material of the cage segments 20 is not limited to this.
[0023] Fig. 3 is a perspective view of the inner ring assembly As, showing only one retainer segment 20. In the following description, the retainer segment 20 may be simply referred to as "segment 20". As shown in Fig. 5, the segment 20 has a large diameter side arcuate portion 22 and a small diameter side arcuate portion 21 that extend in the circumferential direction, and a plurality of pillar portions 23 that connect these large diameter side and small diameter side arcuate portions 22, 21. The small diameter side arcuate portion 21 and the large diameter side arcuate portion 22 face each other at a predetermined distance, and the plurality of pillar portions 23 are provided between the small diameter side arcuate portion 21 and the large diameter side arcuate portion 22.
[0024] A pocket 16 that accommodates a tapered roller 15 (FIG. 4) is formed by a space surrounded by two adjacent column portions 23, 23, the small diameter side arcuate portion 21, and the large diameter side arcuate portion 22. In this embodiment, six column portions 23 are provided in one segment 20, and five pockets 16 are provided lined up in the circumferential direction. However, the number of pockets 16 is not limited to this, and it is sufficient that a plurality of pockets 16 are provided in one segment 20 in the circumferential direction.
[0025] As shown in Fig. 4, of the five pockets 16, two pockets 16, 16 other than the pockets at both circumferential ends and the pocket in the circumferential middle have first guide claws 24a extending from the pillar portions 23 to the inner diameter side. The first guide claws 24a prevent the tapered rollers 15 from slipping out to the inner diameter side. The pockets 16, 16 at both circumferential ends and the pocket 16 located in the circumferential middle have second guide claws 24b extending from the pillar portions 23 to the outer diameter side. The second guide claws 24b prevent the tapered rollers 15 from slipping out to the outer diameter side.
[0026] Roller guide surfaces 24aa, 24ba, which are the inner circumferential surfaces of first and second guide claws 24a, 24b, have a concave shape curved along the shape of tapered rollers 15. Due to these guide claws 24a, 24b, cage 17 is guided only by tapered rollers 15 during operation. In other words, the tapered roller bearing of this embodiment can achieve roller guidance.
[0027] In each pocket 16 having second guide claws 24b extending from the column portion 23 to the outer diameter side, the tapered rollers 15 are inserted from the inner diameter side of the segment 20. In each pocket 16 having second guide claws 24b, the second guide claws 24b prevent the tapered rollers 15 from slipping out to the outer diameter side. In each pocket 16 having second guide claws 24b, in the state of the inner ring assembly As in Figure 3, the raceway surface 13 of the inner ring 11 is located on the inner diameter side, so the tapered rollers 15 do not slip out to the inner diameter side either.
[0028] As shown in Fig. 4, in the pockets 16, 16 having the first guide claws 24a extending from the pillar portions 23 to the inner diameter side, the tapered rollers 15 can be inserted from the outer diameter side of the segment 20. In the state of the inner ring assembly As shown in Fig. 3, the raceway surface 13 of the inner ring 11 is located on the inner diameter side, so the tapered rollers 15 do not slip out to the inner diameter side, but the tapered rollers 15 accommodated in the two pockets 16, 16 other than the pockets at both circumferential ends and in the middle in the circumferential direction shown in Fig. 4 may fall out to the outer diameter side.
[0029] <Fall prevention parts> In this embodiment, as shown in Fig. 3, a drop-out prevention member 32 is provided along the outer diameter surface of the second guide claws 24b in the two pockets 16, 16. This drop-out prevention member 32 prevents the tapered rollers 15 from dropping off to the outer diameter side. The drop-out prevention member 32 is made of, for example, resin or metal. However, the material of the drop-out prevention member 32 is not limited to this.
[0030] As shown in Fig. 6, the anti-disengagement member 32 is detachably attached to the segment 20 and has a columnar portion 32a, a base portion 32b, and first and second segment engaging portions 32c and 32d. The columnar portion 32a extends along the outer diameter surface of the segment 20. The base portion 32b extends along the large diameter side surface 22b of the segment 20. The first segment engaging portion 32c engages with the inner diameter surface of the segment 20. The second segment engaging portion 32d engages with the end face of the large diameter side protrusion (protrusion) 26 of the segment 20.
[0031] In this embodiment, the columnar portion 32a extends along the outer diameter surface 22a of the large diameter side arcuate portion 22 and the outer diameter surface of the second guide claw 24b in the pocket 16. The columnar portion 32a abuts against the outer diameter surface of the second guide claw 24b and the tapered roller 15 (FIG. 3), respectively, to prevent the tapered roller 15 (FIG. 3) from falling off. The contact surface 32aa of the columnar portion 32a with the tapered roller 15 (FIG. 3) is a concave shape curved along the outer shape of the tapered roller 15 (FIG. 3). The contact surface 32ab of the columnar portion 32a with the second guide claw 24b is also a concave shape curved along the outer diameter surface of the second guide claw 24b.
[0032] The base 32b abuts against the large diameter side surface 22b of the large diameter side arcuate portion 22. The first segment engaging portion 32c is a claw-shaped member extending from the base 32b toward the small diameter side, and engages with the inner diameter surface 22c of the large diameter side arcuate portion 22. The second segment engaging portion 32d extends a predetermined small distance from the side surface of the base 32b in a direction perpendicular to this side surface, and engages with the end face of the large diameter side protrusion 26.
[0033] The columnar portion 32a contacts the outer diameter surface of the second guide claw 24b and the tapered roller 15 (FIG. 3), and the first segment engagement portion 32c engages with the inner diameter surface 22c of the large diameter side arcuate portion 22. This limits the radial movement of the fall-off prevention member 32. The columnar portion 32a contacts the outer diameter surface of the second guide claw 24b and the tapered roller 15 (FIG. 3), and the second segment engagement portion 32d engages with the end face of the large diameter side protrusion portion 26. This limits the movement of the fall-off prevention member 32 in the circumferential direction.
[0034] As shown in Figs. 6 and 7, the anti-disengagement member 32 has a guide portion 35 with which the connecting member 25 is engaged. The guide portion 35 is provided on the base portion 32b of the anti-disengagement member 32. More specifically, the guide portion 35 is provided on the side of the base portion 32b of the anti-disengagement member 32 opposite to the surface that abuts against the segment 20. The guide portion 35 is an engagement groove with which the connecting member 25 is engaged. More specifically, the guide portion 35 is a groove that opens radially outward. However, the shape of the guide portion 35 is not limited thereto. For example, the guide portion 35 may be an insertion hole (not shown) through which the connecting member 25 is inserted.
[0035] 5 and 6, large diameter side protrusions 26 are provided on both end sides of the large diameter side surface 22b of the large diameter side arcuate portion 22. The large diameter side protrusions 26 protrude in the axial direction from the large diameter side surface 22b of the large diameter side arcuate portion 22. The large diameter side protrusions 26 have engagement portions 27 with the connecting member 25. In this embodiment, the engagement portions 27 are engagement grooves into which the connecting member 25 is fitted. The large diameter side protrusions 26 are positioned so as not to interfere with the anti-disengagement member 32.
[0036] 3, the large diameter side protrusion 26 and the fall-off prevention member 32 are positioned side by side in the circumferential direction, and the engagement portion 27 of the large diameter side protrusion 26 is connected to the guide portion 35 (FIG. 5) of the fall-off prevention member 32. The cage segments 20 and the fall-off prevention members 32 are connected by engaging and fastening the connecting member 25 with the engagement portion 27 and the guide portion 35 (FIG. 5).
[0037] <About connecting parts> The connecting member 25 is detachable from the segments 20 and the fall-off prevention member 32, and prevents the annularly arranged segment holder 17 from coming apart. The connecting member 25 is, for example, a wire, but may also be a belt or the like. Both ends of the connecting member 25 are connected by a fastening portion or fastening member. By arranging the connecting member 25 close to the large diameter side arc-shaped portion 22 of the cage 17, a gap is secured that allows the connecting member 25 to be removed by hand or with a tool after the bearing is assembled. The fastening portion or fastening member is preferably arranged between the large diameter side protrusions 26, 26 on both ends of the large diameter side arc-shaped portion 22 of the segment 20.
[0038] The connecting member 25 may be a single continuous piece, but the connecting member 25 may be divided into multiple pieces, and the ends of each connecting member 25 may be connected by fastening parts or fastening members 42 shown in Fig. 10. In this case, it is preferable that the multiple fastening parts and fastening members 42 are arranged at equal intervals on a circumference. The fastening parts or fastening members 42 allow the fastening force to be applied evenly to the entire connecting member 25.
[0039] When a wire is used as the connecting member 25, a hook or a turnbuckle can be used as the fastening member 42. A turnbuckle is preferable because it is detachable, the fastening force does not loosen, and the fastening force is adjustable. When a wire is used as the connecting member 25, a detachable buckle is preferable because the fastening force does not loosen.
[0040] When a turnbuckle is used as the fastening member 42, the fastening member 42 has a body with a female thread, and a male thread provided on the end of the connecting member 25 can be screwed into this body to connect the ends of the connecting members 25. By rotating the body of the turnbuckle 42, tension can be applied to the connecting member 25, and by rotating it in the reverse direction, the binding of both ends of the connecting member 25 can be released.
[0041] <Regarding ring jigs, etc.> 7, the small diameter side arcuate portion 21 of the segment 20 has a jig engagement surface 21a that can engage with the annular jig 31 without a groove or protrusion structure. In other words, the outer diameter surface of the small diameter side arcuate portion 21 also serves as the jig engagement surface 21a that engages with the annular jig 31. When the large diameter sides of the segments 20 are bound together with the connecting member 25, the annular jig 31 engaged with the jig engagement surface 21a prevents the small diameter sides of the segments 20 from expanding due to tightening of the connecting member 25. The annular jig 31 can be freely attached to and detached from the segment 20 by, for example, a bolt or the like.
[0042] The annular jig 31 has an annular base 31a, a cylindrical portion 31b, and an engaged portion 31c, which are integrally formed from resin or metal. In FIG. 7, the overall shape of the annular jig 31 is an annular shape, not a partial arc shape. The annular base 31a is detachably attached to the small end face 11b of the inner ring 11, and has a rectangular cross section extending a predetermined distance in the axial direction from the small end face 11b. The cylindrical portion 31b is a cylindrical member extending from the tip of the annular base 31a to the outer diameter side. The engaged portion 31c extends from the outer diameter side edge of the cylindrical portion 31b toward one axial direction A1 so as to be inclined toward the outer diameter side. The annular base 31a, the cylindrical portion 31b, and the engaged portion 31c form the annular jig 31 having a substantially concave cross section. The inner peripheral surface of the engaged portion 31c becomes the engaged surface that engages with the jig engagement surface 21a. When the annular jig 31 is attached to the segment 20, the engaged surface is parallel to the jig engaging surface 21a, which is the outer diameter surface of the small diameter side arcuate portion 21.
[0043] <Tapered roller bearing assembly procedure> First, as shown in Fig. 3, the inner ring assembly As is assembled by integrating the inner ring 11, tapered rollers 15, and cage 17. To assemble the inner ring assembly As, first, with the large end face 11a of the inner ring 11 facing down, the segments 20, tapered rollers 15, and anti-fall-out members 32 are arranged one revolution on the raceway surface 13 of the inner ring 11, as shown in Fig. 9. If the tapered rollers 15 are placed on the raceway surface 13 of the inner ring 11 with the large end face 11a of the inner ring 11 facing down, there is a possibility that the tapered rollers 15 will fall off due to their own weight. To prevent this from happening, as shown in Fig. 8, the distance from the center axis AX1 of the inner ring 11 to the tip of the large rib portion 19 is made greater than the distance from the center axis AX1 of the inner ring 11 to the center of gravity C1 of the tapered rollers 15.
[0044] In detail, with tapered rollers 15 arranged on raceway surface 13 of inner ring 11 with large end face 11a of inner ring 11 facing down, the angle at which large rib portion 19 of inner ring 11 intersects with central axis AX1 of inner ring 11 at a right angle is I, the chamfer width at the tip of large rib portion 19 is H, the distance from central axis AX1 of inner ring 11 to center of gravity C1 of tapered roller 15 is y1, and the diameter of large rib portion 19 is J, the following formula (1) is satisfied. (J / 2)-H cosI>y1 (1)
[0045] Next, as shown in Figure 10, the connecting member 25 is engaged with the engaging portion 27 of the large diameter side protrusion 26 of the segment 20, and the ends of the connecting member 25 arranged on the outer diameter side of the segment 20 are fastened together with the fastening member 42. The connecting member 25 is then tightened by the fastening member 42. This integrates the multiple segments 20 arranged in a ring shape. Then, the annular jig 31 is detachably attached to the small end face (small diameter side face) 11b of the inner ring 11 by bolting or the like. This completes the assembly of the inner ring assembly As.
[0046] After the assembly of the inner ring assembly As is complete, it is fitted to the outer ring 12 (Fig. 1). The inner ring assembly As can be fitted to the outer ring 12 (Fig. 1) in an inverted state with the small diameter side of the inner ring assembly As facing downwards. Even in the inverted state, the jig engagement surface 21a of the segment 20 is held down by the annular jig 31, preventing the inner ring assembly As from coming apart due to the load caused by inversion. When fitting the inner ring assembly As to the outer ring 12 (Fig. 1), the annular jig 31 is removed before assembly.
[0047] Even if the inner ring assembly As is inverted with the annular jig 31 removed, the tapered rollers 15 are sandwiched between the large rib portion 19 and the small rib portion 18, and the tapered rollers 15 are caught by the small rib portion 18, preventing each segment 20 from falling off. When tapered roller 15 is not in contact with large rib portion 19, tapered roller 15 rotates in the direction of arrow AR1 around point A on raceway surface 13, as shown in Figure 11. When tapered roller 15 is in contact with large rib portion 19, it is considered that tapered roller 15 rotates in the direction of arrow AR2 around point B on the inner surface of large rib portion 19, as shown in Figure 12.
[0048] When tapered roller 15 rotates around point B, the small diameter side end face of tapered roller 15 comes into contact with point C on the side face of small rib portion 18. This suppresses the rotation of tapered roller 15. Here, point C is the contact point where the side face of small rib portion 18 and the small diameter side end face of tapered roller 15 come into contact when tapered roller 15 is rotated around the tip of large rib portion 18 of inner ring 11. In other words, contact point C is the intersection point between the spline curve that traces the trajectory of the corner portion of the small end face of tapered roller 15 when tapered roller 15 rotates and the side face of small rib portion 18.
[0049] When the retainer segments 20 (FIG. 10) are connected by the connecting member 25 (FIG. 10), the diameter of the small rib portion 18 of the inner ring 11 shown in FIG. 12 is M, the angle of the small rib portion 18 relative to a line perpendicular to the central axis AX1 of the inner ring 11 is L, the chamfer width of the tip of the small rib portion 18 is K, and the distance from the contact point C to the central axis AX1 is y3, the following formula (2) is satisfied. (M / 2)-K cosL>y3 (2)
[0050] 1, the connecting members 25 and the fall-off prevention members 32 (Fig. 10) can be removed by loosening the fastening parts or fastening members 42 (Fig. 10). After the tapered roller bearing 1 is assembled, the segments 20 will not come apart even if the connecting members 25 and the fall-off prevention members 32 (Fig. 10) are removed.
[0051] <Action and effect> In the conventional structure, in order to provide the cage segments with a surface that engages with the annular jig, a small diameter side protrusion is provided on the small diameter side surface of the small diameter side arcuate portion. In contrast, in the tapered roller bearing 1 of this embodiment, as shown in Figure 7, the outer diameter surface of the small diameter side arcuate portion 21 of the retainer segment 20 also serves as a jig engagement surface 21a that engages with the annular jig 31. This makes it possible to prevent the retainer 17 and tapered rollers 15 from undesirably coming apart when the inner ring assembly is turned over, without providing a small diameter side protrusion. Therefore, the amount of lubricant scooped out by the retainer 17 when the tapered roller bearing 1 (Figure 1) rotates can be reduced compared to the conventional structure, without restricting the bearing size.
[0052] <Other embodiments> In the following description, parts corresponding to matters previously described in each embodiment are given the same reference numerals, and duplicated description is omitted. When only a part of the configuration is described, the other parts of the configuration are the same as the previously described embodiment unless otherwise specified. The same configuration has the same action and effect. It is possible to combine not only the parts specifically described in each embodiment, but also partially combine embodiments together, provided that there is no particular problem with the combination.
[0053] [Second embodiment: FIG. 13] As shown in Fig. 13, the segment 20 may have a structure in which all guide claws for holding the tapered rollers are extended to the outer diameter side to form second guide claws 24b. In this case, there is no anti-fall-out member to prevent the tapered rollers from falling out to the outer diameter side, and the segment 20 is guided by the tapered rollers and the outer ring.
[0054] [Third embodiment: Figs. 14-15] As shown in Figures 14 and 15, the segment 20 may have a structure in which the pockets 16, 16 at both circumferential ends have first guide claws 24a extending from the pillar portion 23 to the inner diameter side, and the central three pockets 16 other than those at both ends have second guide claws 24b extending from the pillar portion 23 to the outer diameter side. In this case, the drop-out prevention members 32 are provided along the outer diameter surfaces 23a of the pillar portions 23 at both ends of the segment 20. Drop-out prevention member guide portions 33 are provided at the circumferential ends of the large diameter side arc-shaped portions 32 of the segment 20. The drop-out prevention member guide portions 33 limit the circumferential movement of the drop-out prevention members 32. The drop-out prevention member 32 can be inserted into and removed from the segment 20 from the large end face side of the inner ring along the drop-out prevention member guide portions 33.
[0055] <Application to wind power generation equipment> FIG. 16 shows an example of a wind turbine generator using a tapered roller bearing 1 according to any one of the embodiments. In this wind turbine generator, a main shaft 53 of a propeller-type wind turbine 52 is rotatably supported by a tapered roller bearing 1, which serves as a main shaft bearing, in a nacelle 51 that is installed on the upper end of a support 50 so as to be able to rotate horizontally. The main shaft bearing is a large bearing with an outer diameter of 1 m or more. The main shaft 53 is connected to a generator 54 via a gearbox 55. The tapered roller bearing 1 according to the embodiment is used for the main shaft bearing in this wind turbine generator. In this case, the tapered roller bearing 1, which is not limited in bearing size and has excellent lubricity, can be applied to large bearings used in wind power generation equipment, and the maintenance costs of the tapered roller bearing 1 can be reduced.
[0056] Although the embodiment for carrying out the present invention has been described above, the embodiment disclosed herein is illustrative in all respects and is not restrictive. The scope of the present invention is indicated by the claims, not by the above description, and is intended to include all modifications within the meaning and scope of the claims. [Explanation of symbols]
[0057] 1... tapered roller bearing, 11... inner ring, 11a... large end face, 11b... small end face (small diameter side surface), 12... outer ring, 15... tapered roller, 16... pocket, 17... cage, 18... small rib portion, 19... large rib portion, 20... cage segment, 21... small diameter side arc-shaped portion, 21a... jig engagement surface, 22... large diameter side arc-shaped portion, 23... column portion, 25... connecting member, 26... large diameter side protruding portion (protruding portion), 27... engagement portion, 31... annular jig, 42... fastening member
Claims
1. The bearing comprises an inner ring, an outer ring, a plurality of tapered rollers interposed between the inner ring and the outer ring, and a retainer for retaining the tapered rollers, the retainer having a plurality of retainer segments divided in the circumferential direction, and the retainer segments are connected by a detachable connecting member, the retainer segment has a large diameter side arcuate portion and a small diameter side arcuate portion extending in a circumferential direction, and a plurality of column portions connecting the large diameter side and small diameter side arcuate portions, the large diameter side arcuate portion, the small diameter side arcuate portion and the column portions forming pockets for accommodating a plurality of the tapered rollers, A tapered roller bearing including a protrusion having an engagement portion with the connecting member on a large diameter side surface of the large diameter side arcuate portion, The outer diameter surface of the small diameter side arcuate portion of the tapered roller bearing also serves as a jig engagement surface that engages with an annular jig.
2. 2. A tapered roller bearing according to claim 1, wherein both ends of the connecting member are connected by a fastening portion or a fastening member.
3. 2. The tapered roller bearing according to claim 1, wherein the connecting member is divided into a plurality of connecting members, and ends of the connecting members are connected by fastening portions or fastening members.
4. 3. The tapered roller bearing according to claim 1, wherein the annular jig is attached to a small diameter side surface of the inner ring.
5. 5. A tapered roller bearing according to claim 4, wherein said annular jig is detachably attached to said inner ring.
6. 3. The tapered roller bearing according to claim 1, wherein the cage segments are made of polyetheretherketone containing carbon fiber or polyetheretherketone containing glass fiber.
7. 3. A tapered roller bearing according to claim 1 or 2, wherein, with the tapered rollers arranged on the raceway surface of the inner ring with the large end face of the inner ring facing down, the angle at which the large rib portion of the inner ring intersects with the central axis of the inner ring at a right angle is I, the chamfer width of the tip of the large rib portion is H, the distance from the central axis of the inner ring to the centre of gravity of the tapered roller is y1, and the diameter of the large rib portion is J, satisfying the following conditions: (J / 2)-H・cosI>y1
8. 3. A tapered roller bearing according to claim 1 or 2, wherein, with the retainer segments connected by the connecting member, the diameter of the small rib portion of the inner ring is M, the angle that the small rib portion makes with a line perpendicular to the central axis of the inner ring is L, the chamfer width of the tip of the small rib portion is K, and the distance from a contact point C at which the side of the small rib portion and the small diameter end face of the tapered roller come into contact with each other when the tapered roller is rotated around the tip of the large rib portion of the inner ring, to the central axis is y3, which satisfies the following condition: (M / 2)-K cosL>y3
9. 3. The tapered roller bearing according to claim 1 or 2, which is a large-sized bearing having an outside diameter of 1 m or more, used in a wind power generating device.
Citation Information
Patent Citations
Roller bearing cage
EP1408248A2
Transonic compressor
JP2009052476A
Conical roller bearing
JP2022179448A
Conical roller bearing
JP2022179449A