Tapered roller bearing

Abstract

To provide a tapered roller bearing that prevents the inner ring assembly from falling apart. [Solution] The cage of the tapered roller bearing is constructed by arranging a plurality of cage segments in the circumferential direction, and an inner ring assembly As can be assembled in which the inner ring 11, a plurality of tapered rollers 15 and the cage are integrated. The following equations (1) and (2) are satisfied. D≦0.008E …Equation (1), (φF-φG) / 2≧0.1H …Equation (2) In equation (1), "D" is the distance between the small end face 15b of the tapered roller 15 and the small flange 18 of the inner ring 11 when the large end face 15a of the tapered roller 15 is in contact with the large flange 19 of the inner ring 11, and "E" is the roller length of the tapered roller 15. In equation (2), "F" is the outer diameter of the small flange of the inner ring 11, "G" is the small end diameter of the raceway surface of the inner ring 11, and "H" is the small end diameter of the tapered roller 15.

Description

Technical Field

[0001] The present invention relates to a tapered roller bearing for the main shaft of a wind power generation device, a tapered roller bearing for industrial machinery, particularly a large tapered roller bearing with an outer diameter exceeding 1 m.

Background Art

[0002] For tapered roller bearings, a cage made of a steel plate is usually used. The cage made of a steel plate is manufactured, for example, by pressing. However, for a large one with an outer diameter exceeding 1 m, pressing becomes difficult due to equipment problems. On the other hand, for a cage manufactured by machining, the cost increases significantly compared with a pressed product. For this reason, as shown in FIGS. 12 and 13, a resin segment cage 71 capable of suppressing the cost has been proposed (for example, Patent Document 1). In this segment cage 71, a roller 70 is inserted into a pocket Pt in which guide claws 72 extend on the inner diameter side and the outer diameter side.

[0003] When incorporating a single-row tapered roller bearing into a windmill, there is a process of handling an inner ring assembly in which an inner ring, tapered rollers, and a cage are integrated with the small end face of the inner ring facing downward. At this time, a method has been proposed in which the segment cage is connected and integrated with a connecting member such as a wire so that the segment cage and the tapered rollers do not fall off from the inner ring (Patent Documents 2 and 3).

Prior Art Documents

Patent Documents

[0006] The object of the present invention is to provide a tapered roller bearing that prevents the inner ring assembly from falling apart. [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 and outer rings, and a cage that holds the tapered rollers, wherein the cage is constructed by arranging a plurality of cage segments in the circumferential direction, and the inner ring assembly, in which the inner ring, the plurality of tapered rollers, and the cage are integrated, can be assembled. A tapered roller bearing that satisfies the following equations (1) and (2). D≦0.008E …Formula (1) (φF-φG) / 2≧0.1H …Equation (2)

[0008] However, in equation (1), "D" is the distance between the small end face of the tapered roller and the small flange of the inner ring when the large end face of the tapered roller is in contact with the large flange of the inner ring, and "E" is the length of the tapered roller. In equation (2), "F" is the outer diameter of the small flange of the inner ring, "G" is the small end diameter of the raceway surface of the inner ring, and "H" is the small end diameter of the tapered roller. The term "integration" refers to the fact that, during bearing assembly, the inner ring, multiple tapered rollers, and cage are treated as a single, temporarily fixed assembly. The aforementioned "roller length" is the axial length of the conical roller. The aforementioned "small flange outer diameter" is the maximum diameter of the small flange portion.

[0009] This configuration, by satisfying equations (1) and (2), can suppress the rotation of the tapered rollers around a point on the inner surface of the large flange portion of the inner ring in the inner ring assembly state. This prevents the tapered rollers from falling out of the retainer segments. Therefore, it is possible to prevent the inner ring assembly from falling apart.

[0010] If the distance D is greater than 0.8% of the roller length E, when the tapered roller rotates around a point on the inner surface of the large flange in the inner ring, it will either not contact the small flange, or the outer diameter F of the small flange will need to be made extremely large in order to make contact. If the outer diameter F of the small flange becomes extremely large, the capacity that can contain lubricant decreases, and the lubrication performance deteriorates. On the other hand, if half the difference between the outer diameter F of the small flange and the small end diameter G of the raceway is less than 10% of the small end diameter H of the roller, then when the tapered roller rotates around a point on the inner surface of the large flange, it will not contact the small flange, or the distance D will need to be made extremely small in order to make contact with the small flange. If the distance D becomes extremely small, there is a concern that the contact between the small flange and the tapered roller will increase during bearing operation, leading to increased wear on the small end face of the roller.

[0011] Generally, tapered roller bearings that use large tapered rollers with a large roller diameter tend to have a smaller flange height relative to the roller diameter. Therefore, Preferably, the length of the tapered roller is 80 mm or more, and the diameter of the tapered roller is 50 mm or more. In a tapered roller bearing using such large tapered rollers, satisfying equations (1) and (2) more effectively suppresses the rotation of the tapered roller around a point on the inner surface of the large flange portion of the inner ring. The aforementioned "roller diameter" is the value obtained by adding the small end diameter and large end diameter of the tapered roller and dividing the result by "2".

[0012] The retainer segment has a plurality of pockets arranged in the circumferential direction for holding the tapered roller, and the retainer segment has a large-diameter side arc-shaped portion and a small-diameter side arc-shaped portion extending in the circumferential direction, and a plurality of columnar portions connecting these large-diameter side and small-diameter side arc-shaped portions, and the pockets are formed by the large-diameter side arc-shaped portion, the small-diameter side arc-shaped portion and the columnar portions. The plurality of retainer segments may be configured such that the large-diameter side arc-shaped portion of each retainer segment can be connected in the circumferential direction, thereby enabling the assembly of the inner ring assembly.

[0013] In this case, the inner ring assembly is assembled by connecting the large-diameter arc-shaped portions of each retainer segment in the circumferential direction. When the inner ring assembly is fitted onto the outer ring, even if the inner ring assembly is inverted with the small-diameter side facing downwards, the tapered rollers catch on the small flange portion, preventing each retainer segment from falling out.

[0014] The plurality of retainer segments are connected by detachable connecting members to the large-diameter side arc-shaped portions, and both ends of the connecting members may be connected by fastening portions or fastening members. This configuration makes it easy to handle the connecting members.

[0015] A fall prevention member may be detachably provided on the large-diameter side arc-shaped portion to prevent the tapered roller held in the pocket from falling out toward the outer diameter side. In the inner ring assembly state, the fall prevention member is attached to the large-diameter side arc-shaped portion of the retainer segment. As a result, the tapered roller that is permitted to be pulled out toward the outer diameter side is prevented from falling out toward the outer diameter side by the fall prevention member.

[0016] The anti-detachment member may have a guide portion into which the connecting member is detachably engaged. In this case, the connecting member is attached to the large-diameter side arc-shaped portion of the retainer segment, and the connecting member is engaged with the guide portion of the anti-detachment member. Furthermore, by connecting both ends of the connecting member, the multiple retainer segments arranged in a ring are integrated into one unit.

[0017] The tapered roller bearing may be a large bearing with an outer diameter of 1 m or more, used in wind power generation equipment. In this case, tapered roller bearings, which have excellent assembly properties, can be applied to large bearings used in wind power generation equipment, and the labor hours and maintenance costs of the tapered roller bearing can be reduced compared to conventional tapered roller bearings. [Effects of the Invention]

[0018] The tapered roller bearing of the present invention includes an inner ring, an outer ring, a plurality of tapered rollers interposed between the inner ring and the outer ring, and a cage for holding the tapered rollers. The cage is configured by arranging a plurality of cage segments in the circumferential direction, and is a tapered roller bearing capable of assembling an inner ring assembly in which the inner ring, the plurality of tapered rollers, and the cage are integrated, and satisfies the following formulas (1) and (2). D ≦ 0.008E … Formula (1) (φF - φG) / 2 ≧ 0.1H … Formula (2) However, in Formula (1), "D" is the distance between the small end face of the tapered roller and the small flange portion of the inner ring in a state where the large end face of the tapered roller is in contact with the large flange portion of the inner ring, "E" is the roller length of the tapered roller, and in Formula (2), "F" is the outer diameter of the small flange of the inner ring, "G" is the small end diameter of the raceway surface of the inner ring, and "H" is the small end diameter of the tapered roller. Therefore, it is possible to prevent the inner ring assembly from coming apart.

Brief Description of the Drawings

[0019] [Figure 1] It is a longitudinal sectional view of a tapered roller bearing according to a first embodiment of the present invention. [Figure 2] It is a front view of the inner ring assembly of the tapered roller bearing as viewed from the axial direction. [Figure 3] It is a perspective view of the inner ring assembly. [Figure 4] It is a sectional view of a cage segment in the tapered roller bearing. [Figure 5] It is a perspective view of the inner ring assembly with a dropout prevention member and a connecting member attached. [Figure 6] It is a schematic diagram showing the rotation state of the tapered rollers arranged on the raceway surface of the inner ring. [Figure 7] It is a schematic diagram showing the relationship between the height of the small flange portion of the inner ring and the tapered roller when the tapered roller arranged on the raceway surface of the inner ring is rotated. [Figure 8] It is a diagram showing the parameters of the main part of the inner ring assembly. [Figure 9]This is a cross-sectional view showing the inner ring assembly being assembled onto the outer ring. [Figure 10] This is a cross-sectional view showing the inner ring assembly assembled onto the outer ring. [Figure 11] This is a cutaway perspective view of a wind power generation device using tapered roller bearings according to one embodiment of the present invention. [Figure 12] This is a cross-sectional view of a conventional retainer segment. [Figure 13] This is a perspective view of the retainer segment. [Modes for carrying out the invention]

[0020] [First Embodiment] A tapered roller bearing according to an embodiment of the present invention will be described with reference to Figures 1 to 10. This tapered roller bearing is applicable, for example, to the main shaft of a wind power generation device or to large tapered roller bearings with an outer diameter exceeding 1 m for industrial machinery. However, the applications of the tapered roller bearing are not limited to these.

[0021] <Overall structure of tapered roller bearing> As shown in Figure 1, the tapered roller bearing 1 comprises an inner ring 11, an outer ring 12, a plurality of tapered rollers 15 interposed between the inner and outer rings 11 and 12, and a cage 17 that holds the tapered rollers 15 at regular intervals. The cage 17 has radially opening pockets 16, and the tapered rollers 15 are held in these pockets 16.

[0022] In this specification, 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 direction around the bearing center axis AX is referred to as the "circumferential direction." Furthermore, the side facing the bearing center axis AX is referred to as the "inner diameter side," and the side moving away from the bearing center axis AX is referred to as the "outer diameter side." In addition, the direction in which the diameter of the raceway surface 14 of the outer ring 12 decreases in the axial direction is referred to as the "small diameter side," and the direction in which the diameter of the raceway surface 14 increases is referred to as the "large diameter side."

[0023] The outer ring 12 has a raceway surface 14 on its inner circumference on which the tapered rollers 15 roll. The inner ring 11 has a raceway surface 13 on its outer circumference on which the tapered rollers 15 roll, and a large flange portion 19 and a small flange portion 18 on both sides in the axial direction, flanking the raceway surface 13, on which the end faces of the tapered rollers 15 come into contact. Figure 2 is a front view from the axial direction of the inner ring assembly As, which integrates the inner ring 11, the cage 17, and the multiple tapered rollers 15. The tapered roller bearing 1 (Figure 1) is configured to allow the inner ring assembly As to be assembled.

[0024] <Retainer segment> The retainer 17 is constructed by arranging a plurality of retainer segments 20 in the circumferential direction. More specifically, the plurality of retainer segments 20 are connected by a connecting member 25 (Figure 1), which will be described later, to form the retainer 17. The retainer segment 20 in this embodiment is made of resin. More specifically, the retainer segment 20 is, for example, polyetheretherketone compounded with carbon fibers or polyetheretherketone compounded with glass fibers. However, the material of the retainer segment 20 is not limited to these.

[0025] Figure 3 shows only one retainer segment 20 in the inner ring assembly As. The retainer segment 20 has multiple circumferentially arranged pockets 16 for housing the tapered rollers 15. In the following description, the retainer segment 20 may be simply referred to as "segment 20".

[0026] As shown in Figures 3 and 4, the segment 20 has a large-diameter side arc-shaped portion 22 and a small-diameter side arc-shaped portion 21 extending in the circumferential direction, and a plurality of column portions 23 connecting these large-diameter and small-diameter side arc-shaped portions 22 and 21. The small-diameter side arc-shaped portion 21 and the large-diameter side arc-shaped portion 22 are opposite each other at a predetermined distance, and a plurality of column portions 23 are installed between the small-diameter side arc-shaped portion 21 and the large-diameter side arc-shaped portion 22. The plurality of segments 20 are configured such that the large-diameter side arc-shaped portions 22 of each segment 20 can be connected in the circumferential direction, thereby enabling the assembly of an inner ring assembly As.

[0027] A pocket 16 for housing the cone roller 15 is formed by the space enclosed by two adjacent columnar sections 23, 23, a small-diameter side arc-shaped section 21, and a large-diameter side arc-shaped section 22. In this embodiment, four columnar sections 23 are provided in one segment 20, and three pockets 16 are provided arranged in the circumferential direction. However, the number of pockets 16 is not limited to this, and three or more pockets may be provided in the circumferential direction in one segment 20.

[0028] As shown in Figure 4, of the three pockets 16, the pocket 16 in the circumferential direction center has a first guide claw 24a extending inward from the column portion 23. The pockets 16, 16 at both ends in the circumferential direction have second guide claws 24b extending outward from the column portion 23. The first guide claw 24a prevents the tapered roller 15 from coming out (falling out) inward, and the second guide claw 24b prevents the tapered roller 15 from coming out (falling out) inward.

[0029] The roller guide surfaces 24aa and 24ba, which are the inner circumferential surfaces of the first and second guide claws 24a and 24b, have a concave shape that is curved along the shape of the tapered roller 15. Due to these guide claws 24a and 24b, the cage 17 is guided only by the tapered roller 15 during operation. In other words, the tapered roller bearing of this embodiment can achieve roller guidance.

[0030] The tapered rollers 15 can be inserted into the pockets 16, 16 at both ends in the circumferential direction from the inner diameter side of the segment 20. The second guide claw 24b prevents the tapered rollers 15 from coming out to the outer diameter side. Also, in the state of the inner ring assembly As shown in Figure 3, the raceway surface 13 of the inner ring 11 is located on the inner diameter side, so the tapered rollers 15 cannot come out to the inner diameter side either.

[0031] As shown in Figure 4, the tapered roller 15 can be inserted into the pocket 16 in the circumferential center from the outer diameter side. In the state of the inner ring assembly As shown in Figure 3, the raceway surface 13 of the inner ring 11 is located on the inner diameter side, so the tapered roller 15 will not come out on the inner diameter side. However, the tapered roller 15 housed in the pocket 16 in the circumferential center as shown in Figure 4 may fall out on the outer diameter side. In this embodiment, as shown in Figure 3, a fall-prevention member 32 is provided along the outer diameter surface 23a of one of the columnar portions 23 that constitute the pocket 16 in the circumferential center, the outer diameter surface 22a of the large diameter side arc-shaped portion 22, etc.

[0032] <Anti-detachment component> As shown in Figure 5, the anti-drop member 32 prevents the tapered roller 15 held in the pocket 16 from falling out toward the outer diameter side. In other words, the anti-drop member 32 prevents the tapered roller 15 held in the pocket 16 having the first guide claw 24a (Figure 4) from falling out toward the outer diameter side. The anti-drop member 32 is detachably provided on the large-diameter side arc-shaped portion 22 of the segment 20. As shown in Figure 3, the anti-drop member 32 can be inserted and removed from the inner ring large end face side shown in Figure 5, along the second guide claw 24b extending toward the outer diameter side of adjacent pockets 16. The anti-drop member 32 is made of, for example, resin or metal. However, the material of the anti-drop member 32 is not limited to these.

[0033] As shown in Figures 3 and 5, the fall prevention member 32 has a columnar portion 32a, a segment engaging portion 32c, a beam portion 32e, and a guide portion 32f, which are integrally provided. The phrase "integrally provided" means that the columnar portion 32a, the segment engaging portion 32c, the beam portion 32e, and the guide portion 32f are not made by combining multiple elements, but are formed from a single material, for example, by molding using a mold, machining, etc., as part of or as a whole of a single object.

[0034] The columnar portion 32a extends along the outer diameter surface of the segment 20 and contacts the outer diameter surface of the tapered roller 15. The columnar portion 32a extends along the outer diameter surface 22a of the large diameter side arc portion 22 and the outer diameter surface 23a of the columnar portion 23. The columnar portion 32a abuts against the outer diameter surface of the tapered roller 15 to prevent the tapered roller 15 from falling off. In this embodiment, the contact surface 32aa of the columnar portion 32a with the tapered roller 15 is a concave shape that is curved along the outer diameter surface of the tapered roller 15.

[0035] The segment engagement portion 32c is a substantially concave portion that extends along the outer diameter surface 22a, the large diameter side surface 22b, and the inner diameter surface 22c of the segment 20, and engages with the outer diameter surface 22a, the large diameter side surface 22b, and the inner diameter surface 22c of the segment 20. The portion 32cb of the segment engagement portion 32c that engages with the inner diameter surface 22c is a claw-shaped portion that extends a predetermined length toward the small diameter side from the main body portion (the portion along the large diameter side surface 22b) 32ca of the segment engagement portion 32c. The segment engagement portion 32c contacts the outer diameter surface 22a and the inner diameter surface 22c of the segment 20, thereby restricting the radial movement of the anti-detachment member 32.

[0036] The columnar portion 32a contacts the outer diameter surface of the tapered roller 15 and the outer diameter surface 24bb of the guide claw, and the segment engaging portion 32c or guide portion 32f contacts the large diameter side projection 26 of the segment 20, which will be described later. This restricts the circumferential movement of the fall prevention member 32. The segment engaging portion 32c contacts the large diameter side surface 22b, and the guide portion 32f contacts the connecting member 25, thereby restricting the axial movement of the fall prevention member 32.

[0037] The beam portion 32e connects the columnar portion 32a and the segment engaging portion 32c at different circumferential positions. The beam portion 32e is positioned on the outer diameter surface 22a of the large-diameter side arc-shaped portion 22. The circumferential length of this beam portion 32e is appropriately set according to the circumferential position of the columnar portion 32a relative to the segment 20, and the circumferential position of the large-diameter side projection 26 of the segment 20, etc.

[0038] A connecting member 25, described later, is detachably engaged with the guide portion 32f. Of the fall prevention member 32, the guide portion 32f is provided on the side of the main body portion 32ca of the segment engaging portion 32c that is opposite to the surface that contacts the segment 20. In this example, the guide portion 32f is a through-hole forming portion that forms an insertion hole 35A through which the connecting member 25 is inserted. The guide portion 32f is not limited to the through-hole forming portion, and may be, for example, a groove forming portion (not shown) that forms a groove that opens radially outward.

[0039] Large-diameter protrusions 26, 26 are provided at both ends of the large-diameter side surface 22b of the large-diameter side arc-shaped portion 22 of the retainer segment 20. These multiple large-diameter protrusions 26, 26 protrude axially for a predetermined length from the large-diameter side surface 22b of the large-diameter side arc-shaped portion 22. Each large-diameter protrusion 26 has an engaging portion 27 into which the connecting member 25 is detachably engaged. In this embodiment, the engaging portion 27 is an engaging groove into which the connecting member 25 is fitted.

[0040] The large-diameter protrusion 26 is positioned so as not to interfere with the anti-detachment member 32. The large-diameter protrusion 26 and the anti-detachment member 32 are positioned side by side in the circumferential direction, and the engaging portion 27 of the large-diameter protrusion 26 and the insertion hole 35A of the guide portion 32f are connected. Each segment 20 and each anti-detachment member 32 are connected by engaging the connecting member 25 with this engaging portion 27 and the insertion hole 35A of the guide portion 32f and tightening it.

[0041] <Regarding connecting components, etc.> Multiple segments 20 are connected by a connecting member 25 that is detachable from the large-diameter side arc-shaped portion 22. The connecting member 25 is detachable from the segments 20 and the anti-detachment member 32, preventing the annularly arranged segment retainer 17 from scattering or dispersing. At the large-diameter side arc-shaped portion 22 of each segment 20, the connecting member 25 is detachably engaged via an engaging portion 27, forming an inner ring assembly As in which the inner ring 11, multiple tapered rollers 15, and retainer 17 are integrated. The connecting member 25 is, for example, a wire. However, the connecting member 25 is not limited to a wire and may be a belt or the like.

[0042] In this embodiment, both ends of the connecting member 25 are connected by a fastening portion or fastening member 42. This configuration makes it easy to handle the connecting member 25. By positioning the connecting member 25 near the large-diameter side arc-shaped portion 22 of the retainer 17, a gap is secured that allows the connecting member 25 to be removed by hand or with a tool after bearing assembly. Furthermore, it is preferable that the fastening portion or fastening member 42 be positioned between one of the multiple (two in this example) large-diameter side protrusions 26, 26 on the large-diameter side arc-shaped portion 22 of the segment 20 and the other large-diameter side protrusions 26.

[0043] The connecting member 25 may be a single continuous piece, or it may be divided into multiple pieces, with the ends of each connecting member 25 connected by fastening parts or fastening members 42. In this case, it is preferable that the multiple fastening parts and fastening members 42 are arranged at equal intervals around the circumference. The fastening parts or fastening members 42 allow for even fastening force to be applied to the entire connecting member 25.

[0044] When a wire is used as the connecting member 25, a hook or turnbuckle can be used as the fastening member 42. A turnbuckle is preferable because it is detachable, does not loosen, and allows for adjustment of the tightening force. When a wire is used as the connecting member 25, a detachable buckle is preferable because it does not loosen the tightening force.

[0045] When a turnbuckle is used as the fastening member 42, the fastening member 42 has a body with a female threaded portion, and the male threaded portion provided at the end of the connecting member 25 can be screwed into this body to connect the ends of the connecting member 25. By rotating the body of the turnbuckle 42, tension can be applied to the connecting member 25, and by rotating it in the opposite direction, the fastening at both ends of the connecting member 25 can be released.

[0046] Here, segment 20 can rotate around the connecting member 25, but the rotation of segment 20 is suppressed by the contact between the first and second guide claws 24a and 24b (Figure 4) of segment 20, the small end face of the pocket, and the large end face of the pocket and the tapered roller 15. On the other hand, as shown in Figure 6, when the conical roller 15 is not in contact with the large flange 19, it rotates in the direction of arrow AR1 around point A on the raceway surface 13. When the conical roller 15 is in contact with the large flange 19, as shown in Figure 7, it rotates in the direction of arrow AR2 around point B on the inner surface of the large flange 19. When the conical roller 15 rotates in this way, the segment 20 in Figure 5 also rotates in conjunction, and it is conceivable that the conical roller 15 will eventually detach from the inner ring assembly As.

[0047] When the tapered roller 15 shown in Figure 7 rotates around point B on the large flange portion 19, the rotation of the tapered roller 15 can be suppressed if the small end face of the tapered roller 15 contacts the side surface of the small flange. To achieve this, as shown in Figure 8, the large end face 15a of the tapered roller 15 is in contact with the large flange portion 19 of the inner ring 11, and the distance D between the small end face 15b of the tapered roller 15 and the side surface of the small flange portion 18 on the inner ring 11 is reduced. In addition, increasing the outer diameter F of the small flange of the inner ring 11 is effective. However, tapered roller bearings, which generally use large tapered rollers with a large roller diameter, tend to have a smaller flange height relative to the roller diameter.

[0048] <Parameters> Therefore, in a tapered roller bearing that uses a large tapered roller 15 with a roller length E of 80 mm or more and a roller diameter of 50 mm or more, the following equations (1) and (2) are satisfied. D≦0.008E …Formula (1) (φF-φG) / 2≧0.1H …Equation (2)

[0049] However, in equation (1), "D" is the distance between the small end face 15b of the tapered roller 15 and the small flange 18 of the inner ring 11 when the large end face 15a of the tapered roller 15 is in contact with the large flange 19 of the inner ring 11, and "E" is the roller length of the tapered roller 15. In equation (2), "F" is the outer diameter of the small flange of the inner ring 11, "G" is the small end diameter of the raceway surface of the inner ring 11, and "H" is the small end diameter of the tapered roller 15. It is more desirable to set equation (1) as 0.001E ≤ D ≤ 0.008E. It is more desirable to set equation (2) as 0.3H ≥ (φF - φG) / 2 ≥ 0.1H.

[0050] <Effects and Effects> With this configuration, by satisfying equations (1) and (2), it is possible to suppress the rotation of the tapered roller 15 around point B on the inner surface of the large flange portion 19 of the inner ring 11 in the state of the inner ring assembly As shown in Figure 7. This prevents the tapered roller 15 from falling out of the retainer segment 20 shown in Figure 5. Therefore, it is possible to prevent the inner ring assembly As from falling apart, and the number of man-hours required for assembly can be reduced compared to the conventional structure.

[0051] If the distance D shown in Figure 8 is greater than 0.8% of the roller length E, then, as shown in Figure 7, when the tapered roller 15 rotates around point B on the inner surface of the large flange 19 in the inner ring 11, it will not contact the small flange 18 shown in Figure 8, or the outer diameter F of the small flange will need to be made extremely large in order to make contact with the small flange 18. If the outer diameter F of the small flange becomes extremely large, the capacity that can contain lubricant will decrease, and the lubrication performance will decline. On the other hand, if half the difference between the outer diameter F of the small flange and the small end diameter G of the raceway surface is less than 10% of the small end diameter H of the roller, then when the tapered roller 15 rotates around point B (Figure 7) on the inner surface of the large flange 19, it will not contact the small flange 18, or the distance D will need to be made extremely small in order for it to contact the small flange 18. If the distance D becomes extremely small, there is a concern that the contact between the small flange 18 and the tapered roller 15 will increase during bearing operation, leading to increased wear on the roller's small end surface 15b.

[0052] As shown in Figures 2 and 5, the multiple segments 20 are configured such that the large-diameter arc-shaped portion 22 of each segment 20 can be connected in the circumferential direction, thereby enabling the assembly of the inner ring assembly As. As shown in Figures 9 and 10, when the inner ring assembly As is fitted onto the outer ring 12, even if the inner ring assembly As is inverted with the small-diameter side facing downwards, the tapered rollers 15 catch on the small flange portion 18, preventing each retainer segment 20 from falling out.

[0053] After the assembly of the tapered roller bearing 1 shown in Figure 10 is complete, the connecting member 25 and the anti-detachment member 32 (Figure 5) can be removed by loosening the fastening member 42 (Figure 5). After the assembly of the tapered roller bearing 1, the segments 20 will not fall apart even if the connecting member 25 and the anti-detachment member 32 (Figure 5) are removed.

[0054] According to this embodiment, since the connecting member 25 and the anti-detachment member 32 shown in Figure 5 are detachable, the inner ring assembly As is integrated with the connecting member 25 and the anti-detachment member 32, but the connecting member 25 and the anti-detachment member 32 can be removed after the bearing is installed. In addition, the retainer 17 shown in Figure 4 is guided only by the tapered rollers 15 during operation by the first and second guide claws 24a and 24b, thus enabling roller guidance.

[0055] <Other Embodiments> In tapered roller bearings using tapered rollers with a roller length of less than 80 mm and a roller diameter of less than 50 mm, the above-described equations (1) and (2) may be satisfied. By satisfying equations (1) and (2), it is possible to suppress the rotation of the tapered rollers around point B (Figure 7) on the inner surface of the large flange portion of the inner ring in the inner ring assembly state. This prevents the tapered rollers from falling out of the cage segments. Therefore, it is possible to prevent the inner ring assembly from falling apart.

[0056] <Examples of application to wind power generation equipment> Figure 11 shows an example of a wind power generation device using a tapered roller bearing 1 according to one of the embodiments. In this wind power generation device, the main shaft 53 of a propeller-type wind turbine 52 is rotatably supported by a tapered roller bearing 1, which is the main shaft bearing, in a nacelle 51 that is installed horizontally rotatably at the upper end of a support column 50. 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 speed increaser 55. In this wind power generation device, a tapered roller bearing 1 according to one of the embodiments is used as the main shaft bearing.

[0057] In this case, the tapered roller bearing 1, which has excellent assembly properties, can be applied to large bearings used in wind power generation equipment, thereby reducing the labor costs and maintenance costs of the tapered roller bearing 1.

[0058] While embodiments for carrying out the present invention have been described above based on the embodiments, the embodiments disclosed herein are illustrative in all respects and are not restrictive. The scope of the present invention is indicated by the claims rather than the foregoing description, and all modifications within the meaning and scope equivalent to the claims are intended to be included. [Explanation of Symbols]

[0059] 1... Tapered roller bearing 11…Inner circle 12…Outer ring 15... Circle dipstick 15a…Large end face 17...Cage 18... Small guard section 19…Otsubabe 20… Retainer segment 21…Small diameter side arcuate part 22...Large diameter side arc-shaped section 23...Column part 25…Connecting member 32... Anti-detachment component 32f…Information department 42… Fastening member As...internal chauffeur

Claims

1. A tapered roller bearing comprising an inner ring, an outer ring, a plurality of tapered rollers interposed between the inner and outer rings, and a cage that holds the tapered rollers, wherein the cage is constructed by arranging a plurality of cage segments in the circumferential direction, and the inner ring assembly, in which the inner ring, the plurality of tapered rollers, and the cage are integrated, can be assembled. A tapered roller bearing that satisfies the following equations (1) and (2). D≦0.008E…Formula (1) (φF−φG) / 2≧0.1H…Formula (2) However, in equation (1), "D" is the distance between the small end face of the tapered roller and the small flange of the inner ring when the large end face of the tapered roller is in contact with the large flange of the inner ring, and "E" is the length of the tapered roller. In equation (2), "F" is the outer diameter of the small flange of the inner ring, "G" is the small end diameter of the raceway surface of the inner ring, and "H" is the small end diameter of the tapered roller.

2. A tapered roller bearing according to claim 1, wherein the length of the tapered roller is 80 mm or more, and the diameter of the tapered roller is 50 mm or more.

3. In the tapered roller bearing according to claim 1 or claim 2, the cage segment has a plurality of pockets arranged in the circumferential direction for holding the tapered roller, the cage segment has a large-diameter side arc-shaped portion and a small-diameter side arc-shaped portion extending in the circumferential direction, and a plurality of columnar portions connecting these large-diameter side and small-diameter side arc-shaped portions, and the pocket is formed by the large-diameter side arc-shaped portion, the small-diameter side arc-shaped portion and the columnar portions, The plurality of cage segments are configured such that the large-diameter arc-shaped portions of each cage segment can be connected in the circumferential direction, thereby enabling the assembly of the inner ring assembly in a tapered roller bearing.

4. A tapered roller bearing according to claim 3, wherein the plurality of cage segments are connected by a connecting member that can be attached to the large-diameter side arc-shaped portion, and both ends of the connecting member are connected by a fastening portion or fastening member.

5. A tapered roller bearing according to claim 4, wherein a fall prevention member for preventing the tapered roller held in the pocket from falling out toward the outer diameter side is detachably provided on the large-diameter side arc-shaped portion.

6. The tapered roller bearing according to claim 5, wherein the anti-detachment member is a tapered roller bearing having a guide portion into which the connecting member is detachably engaged.

7. A tapered roller bearing according to claim 1 or claim 2, wherein the tapered roller bearing is a large bearing with an outer diameter of 1 m or more used in a wind power generation device.

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