JP2017015233A - Rolling bearing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress the generation of noise resulting from the attachment of an external member to a bearing ring of a rolling bearing device.SOLUTION: A rolling bearing device 10 has a first bearing ring 14, a second bearing ring 12 and a plurality of rolling bodies 16 which are arranged between the bearing rings. The first bearing ring 14 comprises a first divided bearing ring 32, a second divided bearing ring 30 and a plurality of fastening bolts 34 which fasten the divided bearing rings to an axial direction. The first bearing ring 14 comprises first attachment bolt holes 50 for first attachment bolts 48 which attach a first outer member 42 existing at one side in the axial direction to the first divided bearing ring 32 side, and second attachment bolt holes 46 for second attachment bolts 44 which attach a second outer member 40 existing at the other side in the axial direction to the second divided bearing ring 30 side. Female screw parts 32b of the first attachment bolt holes 50 and female screw parts 32b of the second attachment bolt holes 46 are formed at the first divided bearing ring 32.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a rolling bearing device.

  One example of the use of a rolling bearing device is to attach a rotating object to the axial end of a free-side race.

  For example, in the CT scan device described in Patent Document 1, the outer race of the rolling bearing device is attached to the main body of the CT scan device. A rotating body that holds the X-ray irradiation device and the X-ray detector is attached to one end in the axial direction of the inner race. A pulley driven to rotate by a motor is attached to the other end of the inner race. As the motor rotates the pulley, the inner raceway rotates, and as a result, the rotating body rotates.

JP 2003-130064 A

  By the way, when a rolling bearing apparatus is a pressurization specification, any one of an inner track ring or an outer track ring is comprised by fastening a some part. By fastening a plurality of parts with fastening bolts, a predetermined pressure is applied from the plurality of parts to each of the plurality of rolling elements arranged between the inner raceway and the outer raceway.

  However, in a rolling bearing device of a pressurized specification, for example, as in the rolling bearing device of a CT scanning device described in Patent Document 1, it is attached to the end in the axial direction of a bearing ring configured by fastening a plurality of parts. On the other hand, when an external member is attached, noise may be generated from the rolling bearing device.

  The inventor has found that the cause of this noise is a change in the pressure applied to the rolling elements. That is, when an external member is attached to the end in the axial direction of the raceway configured by fastening a plurality of parts, the pressure applied to the rolling element can be greatly changed from a predetermined pressure before being attached ( Specifically, the inventor found out the unevenness of pressurization and partial pressurization).

  Therefore, the present invention attaches an external member to the end in the axial direction of the raceway ring that is configured by fastening a plurality of parts while suppressing a change in pressure applied to the rolling element, and thereby a rolling bearing device It is an object to suppress the generation of noise from the ground.

  In order to solve the above technical problem, according to the first aspect of the present invention, between the first race ring, the second race ring, and the first race ring and the second race ring. A plurality of rolling elements arranged in a circumferential direction in the annular space, wherein the first raceway ring is arranged on one side in the axial direction; A second split race ring disposed on the other side in the axial direction; and a plurality of fastening bolts for fastening the first split race ring and the second split race ring in the axial direction. The first and second bearing rings are for a plurality of first mounting bolts for axially attaching a first external member existing on one side in the axial direction to the first divided raceway side. A mounting bolt hole and a compound for mounting in the axial direction a second external member existing on the other side in the axial direction on the second split raceway side. A plurality of second mounting bolt holes for the second mounting bolt, and a female thread portion of the first mounting bolt hole and the second mounting bolt that engage with the first mounting bolt. There is provided a rolling bearing device in which the female thread portions of the second mounting bolt holes to be engaged are both formed in the first split race.

  According to such a 1st aspect, the axial direction of the 1st track ring comprised by fastening the 1st and 2nd divisional ring is suppressed, suppressing the change of the pressurization with respect to a rolling element. The first and second external members can be attached to the end, and thereby noise generation from the rolling bearing device can be suppressed.

  According to the second aspect of the present invention, the first divided raceway ring and the second divided raceway ring are fastened in the axial direction by the plurality of fastening bolts arranged in the circumferential direction, and the first The plurality of first mounting bolt holes are formed in a circumferential direction at one end in the axial direction of one track ring, and the plurality of first mounting bolt holes at the other end in the axial direction of the first track ring. The first and second mounting bolt holes are different from each other in position in the radial direction with respect to the radial position of the fastening bolt. An aspect rolling bearing device is provided.

  According to such a 2nd aspect, it is suppressed that the fastening torque of the 1st and 2nd attachment bolt influences the fastening of the 1st and 2nd division | segmentation track ring by a fastening bolt. As a result, the change of the pressurization with respect to a rolling element is further suppressed.

  Furthermore, according to the 3rd aspect of this invention, the rolling bearing apparatus of the 2nd aspect with which the said 1st and 2nd attachment bolt hole and the said fastening bolt are located in a line with radial direction is provided.

  According to such a 3rd aspect, it is further suppressed that the fastening torque of the 1st and 2nd attachment bolt influences the fastening of the 1st and 2nd divisional ring with a fastening bolt. As a result, the change in pressure applied to the rolling elements is further suppressed.

  Furthermore, according to the fourth aspect of the present invention, the first divided raceway ring includes a convex portion protruding toward the second divided raceway ring, and the second divided raceway ring is the first split raceway ring. From the first aspect, wherein the second mounting bolt hole female thread portion is formed on the convex portion of the first split race ring. A rolling bearing device according to any one of the three aspects is provided.

  According to such a 4th aspect, since the 2nd attachment bolt does not pass largely through the 2nd division race ring, but is formed in the 1st division race ring, it can engage with a screw part. . Thereby, the second mounting bolt can be shortened.

  According to the present invention, it is possible to attach an external member to an axial end of a race ring configured by fastening a plurality of parts while suppressing a change in pressure applied to the rolling element, thereby Generation of noise from the rolling bearing device can be suppressed.

Sectional drawing of the rolling bearing apparatus which concerns on one embodiment of this invention Partial enlarged sectional view of the rolling bearing device shown in FIG. Partial enlarged sectional view of the rolling bearing device with the bolt omitted The figure which shows a part of rolling bearing device seen in the axial direction The figure which shows a part of rolling bearing device of a comparative example seen in the axial direction Sectional drawing along the BB line in FIG. Sectional drawing along the DD line in FIG.

  Hereinafter, a rolling bearing device according to an embodiment of the present invention will be described with reference to the drawings.

  FIG. 1 shows a cross section of a rolling bearing device according to an embodiment of the present invention. FIG. 2 is a partially enlarged sectional view of the rolling bearing device shown in FIG. FIG. 3 is a partially enlarged sectional view of the rolling bearing device in a state where the bolt is omitted. And FIG. 4 is a figure which shows a part of rolling bearing apparatus seen in the axial direction. In the drawing, the X-axis direction indicates the axial direction, that is, the extending direction of the rotation center line C of the rolling bearing device. The Y-axis direction indicates the direction orthogonal to the rotation center line C, that is, the radial direction of the rolling bearing device.

  As shown in FIGS. 1 and 2, the rolling bearing device 10 is disposed in an outer raceway ring 12 (second split raceway) having an annular shape centering on the rotation center line C, and in the outer raceway ring 12. In the annular space between the outer race ring 12 and the inner race ring 14 in the circumferential direction (rotation center line). And a plurality of spherical rolling elements 16 arranged in a state of being spaced apart in the circumferential direction with respect to C). In the case of the present embodiment, the plurality of rolling elements 16 are arranged in two rows (double rows) in the circumferential direction. Moreover, the rolling elements 16 in one row and the rolling elements 16 in the other row are opposed to each other in the axial direction (X-axis direction).

  Further, a retainer 18 that holds each of the plurality of rolling elements 16 in an annular space between the outer raceway ring 12 and the inner raceway ring 14 is provided in the annular space. Furthermore, a shield member 20 is provided between the outer raceway ring 12 and the inner raceway ring 14 in order to suppress the entry of foreign matter into the annular space.

  According to the rolling bearing device 10 having such a configuration, one of the outer race 12 and the inner race 14 rotates relative to the other around the rotation center line C.

  As shown in FIG. 1, in the case of the rolling bearing device 10 according to the present embodiment, the inner bearing ring 14 includes a plurality of parts, specifically, an annular split race 30 having a rotation center line C as the center. , 32 are fastened in the axial direction (X-axis direction). One divided raceway ring 30 (second divided raceway ring) is in contact with the plurality of rolling elements 16 in one row on the outer peripheral side, and the other divided raceway ring 32 (first divided raceway ring) is on the outer peripheral side thereof. To contact the rolling elements 16 in the other row. The split race rings 30 and 32 are fastened in the axial direction by a plurality of fastening bolts 34. As shown in FIG. 4, the plurality of fastening bolts 34 are arranged in a state of being spaced apart in the circumferential direction.

  As shown in FIG. 2, the inner race 14 is formed with a plurality of fastening bolt holes 36 through which the fastening bolts 34 are inserted. As shown in FIG. 3 in which the fastening bolt 34 is omitted, the fastening bolt hole 36 extends in the axial direction (X-axis direction) from the divided raceway ring 30 side.

  Specifically, as shown in FIG. 2, the fastening bolt hole 36 is a through hole having a diameter through which a counterbore portion 30 a that houses the head portion 34 a of the fastening bolt 34 and a shank portion 34 b of the fastening bolt 34 can pass. It is comprised from the part 30b and the internal thread part 32a engaged with the external thread part 34c formed in the front end side of the shank part 34b of the fastening bolt 34. As shown in FIG. Counterbore portions 30 a and through-hole portions 30 b of the fastening bolt holes 36 are formed in the split race 30. The female thread portion 32 a of the fastening bolt hole 36 is formed only in the divided raceway ring 32. A part of the through hole portion of the fastening bolt hole 36 may be formed in the split race ring 32.

  Further, the plurality of fastening bolt holes 36, that is, the plurality of fastening bolts 34 inserted therethrough, are arranged at intervals on the same circumference around the rotation center line C, as shown in FIG. Further, the plurality of fastening bolt holes 36 are formed in the inner race 14 so as to be as close to the rolling element 16 as possible. 1-3 have shown the cross section along the AA in FIG.

  According to such a plurality of fastening bolts 34 and fastening bolt holes 36, the split race rings 30 and 32 are maintained in a state of being in contact with each other in the axial direction (X-axis direction). Further, the divided raceway ring 30 is maintained in a state where the rolling elements 16 in one row are pressed toward the outer raceway ring 12 with a predetermined pressure on the outer peripheral side thereof. Similarly, the divided raceway ring 32 is maintained in a state in which the rolling elements 16 in the other row are pressed toward the outer raceway ring 12 with a predetermined pressure on the outer peripheral side thereof.

  Further, the rolling bearing device 10 is configured to be attachable to an external member as shown in FIG. That is, an external member is attached to the rolling bearing device 10, or the rolling bearing device 10 is attached to the external member.

  Specifically, the outer bearing ring 12 of the rolling bearing device 10 is configured such that the rolling bearing device 10 is connected to an external member, for example, a main body (not shown) of a CT scanning device via a plurality of fixing bolts (not shown). A plurality of through holes 12a are provided for fixing in the axial direction (X-axis direction).

  In contrast, the inner race 14 includes a plurality of mounting bolt holes 46 and 50 for mounting the outer members 40 and 42 to the rolling bearing device 10 via a plurality of mounting bolts 44 and 48. For example, one external member 40 is a rotating body that holds the X-ray irradiation apparatus and the X-ray detector in the CT scanning apparatus. The other external member 42 is a pulley driven by a motor in the CT scanning apparatus.

  As shown in FIG. 1, the external member 40 is attached to the divided raceway 30 side of the inner raceway 14 by a plurality of attachment bolts 44 (second attachment bolts) in the axial direction (X-axis direction). Therefore, a mounting bolt hole 46 (second mounting bolt hole) through which the mounting bolt 44 is inserted is formed so as to extend in the axial direction from the outer member 40 to the inner race ring 14.

  Specifically, as shown in FIG. 3, the mounting bolt hole 46 is a through hole having a diameter through which a counterbore portion 40 a that houses the head portion 44 a of the mounting bolt 44 and a shank portion 44 b of the mounting bolt 44 can pass. Parts 40b and 30c, and a female screw part 32b that engages with a male screw part 44c formed on the front end side of the shank part 44b of the mounting bolt 44.

  A counterbore 40 a and a part 40 b of the through hole of the mounting bolt hole 46 are formed in the external member 40. The remaining portion 30c of the through hole is formed in the split race 30 to which the external member 40 is attached. Although the reason will be described later, the female thread portion 32 b of the mounting bolt hole 46 is formed not on the divided raceway ring 30 but only on the divided raceway ring 32. A part of the through hole portion of the mounting bolt hole 46 may be formed in the split race ring 32.

  As shown in FIG. 1, the external member 42 is attached to the split raceway 32 side of the inner raceway 14 in the axial direction (X-axis direction) by a plurality of attachment bolts 48 (first attachment bolts). Therefore, a mounting bolt hole 50 (first mounting bolt hole) through which the mounting bolt 48 is inserted is formed so as to extend from the outer member 42 to the inner race 14 in the axial direction.

  Specifically, as shown in FIG. 3, the mounting bolt hole 50 has a through hole having a diameter through which a counterbore portion 42 a that houses the head portion 48 a of the mounting bolt 48 and a shank portion 48 b of the mounting bolt 48 can pass. The portion 42 b and a female screw portion 32 b that engages with a male screw portion 48 c formed on the tip end side of the shank portion 48 b of the mounting bolt 48.

  A counterbore 42 a and a through hole 42 b of the mounting bolt hole 50 are formed in the external member 42. The female thread portion 32 b is formed only on the divided raceway ring 32 of the inner raceway ring 14.

  In the case of the present embodiment, as shown in FIG. 2, a male screw portion 44 c for attaching the outer member 40 to the inner raceway 14 and an external thread 42 for attaching the outer member 42 to the inner raceway 14. The male threaded portion 48 c of the mounting bolt 48 engages with a common female threaded portion 32 b formed on the one-piece raceway ring 32. For this purpose, the mounting bolt holes 46 and 50 communicate with each other, whereby the mounting bolts 44 and 48 face each other in the axial direction (X-axis direction).

  From here, as shown in FIG. 2, the internal thread portion 32 b that engages with the mounting bolt 44 for attaching the outer member 40 to the inner race ring 14 is not the split race ring 30 to which the outer member 40 is attached, but the split race ring 30. The reason why it is formed on the race ring 32 will be described. The reason will be described with reference to a comparative example.

  5-7 has shown the rolling bearing apparatus of the comparative example. FIG. 5 shows a part of the rolling bearing device 110 of the comparative example viewed in the axial direction. FIG. 6 shows a cross section of the rolling bearing device 110 of the comparative example along the line BB in FIG. FIG. 7 shows a cross section of the rolling bearing device 110 of the comparative example along the line DD in FIG.

  As shown in FIG. 6, in the rolling bearing device 110 of the comparative example, the inner race ring 114 is configured by the split race rings 130 and 132, and the split race rings 130 and 132 are axially (X-axis direction) by the fastening bolts 134. It is concluded to. A fastening bolt hole 136 through which the fastening bolt 134 is inserted extends in the axial direction from one divided raceway ring 130 toward the other divided raceway ring 132. The female screw hole 132 a of the fastening bolt hole 136 is formed only in the divided raceway ring 132. According to such a configuration, similarly to the embodiment shown in FIGS. 1 to 4, the divided race rings 130 and 132 are maintained in a state of being in contact in the axial direction.

  On the other hand, as shown in FIG. 7, in the rolling bearing device 110 of the comparative example, the attachment of the external members 140 and 142 to the inner race 114 is different from the embodiment shown in FIGS.

  Specifically, the male threaded portion 144c of the mounting bolt 144 for attaching the external member 140 to the split raceway ring 130 is engaged with the female thread portion 130c of the mounting bolt hole 146 formed in the split raceway ring 130. Yes. Further, a male screw portion 148c for attaching the external member 142 to the split raceway ring 132 is formed on the split raceway ring 132 and thus engaged with the screw portion 132b. Therefore, as shown in FIG. 2, the mounting bolt 44 for the external member 40 and the mounting bolt 48 for the external member 42 are formed on one split race ring 32, and thus engage with the screw portion 32b. This is different from the rolling bearing device 10.

  In the case of the rolling bearing device 110 of the comparative example shown in FIG. 7, the external member 140 is fixed to the split race ring 130 via the mounting bolt 144, and the external member 142 is fixed to the split race ring 132 via the mounting bolt 148. . Due to the weight of the external members 140 and 142, forces in directions away from each other act on the divided raceways 130 and 132. Due to the force, the pressurization applied to the plurality of rolling elements 116 from the divided raceways 130 and 132 can greatly change from a predetermined pressurization before the outer members 140 and 142 are attached to the inner raceway 114. If the change in the pressurization varies due to the large change in the pressurization, noise may be generated from the rolling bearing device 110.

  On the other hand, in the case of the rolling bearing device 10 according to the embodiment shown in FIG. 2, the outer member 40 is connected via the mounting bolt 44, and the outer member 42 is connected via the mounting bolt 48. Fixed to. Further, the split race 30 is sandwiched between the external member 40 and the split race 32 in the axial direction (X-axis direction). Therefore, the force in the direction in which the divided race rings 30 and 32 are brought into contact with each other does not act, and the force in the direction in which the divided race rings 30 and 32 are brought into contact acts. Therefore, the pressurization applied to the plurality of rolling elements 16 from the divided raceways 30 and 32 does not substantially change from a predetermined pressurization before the outer members 40 and 42 are attached to the inner raceway 14. As a result, the generation of noise from the rolling bearing device 10 due to a change in pressure is suppressed.

  From here, the configuration of the rolling bearing device that further suppresses the change in the pressure applied to the rolling element from the inner race (divided race) due to the attachment of the external member to the inner race will be described. .

  First, as shown in FIGS. 2 and 4, the mounting bolt holes 46 and 50 (that is, the mounting bolts 44 and 48) are preferably different from the fastening bolt 34 in the radial position (Y-axis direction position). In particular, the mounting bolt holes 46 and 50 (that is, the mounting bolts 44 and 48) and the fastening bolt 34 are more preferably aligned in the radial direction.

  On the other hand, when the fastening bolt 34 and the mounting bolts 44 and 48 are located on substantially the same circumference, when the mounting bolts 44 and 48 are attached to the inner race 14, depending on the conditions, the fastening bolt 34 There is a case where the fastening of the split race rings 30 and 32 by is affected. That is, when the fastening bolt 34 is sandwiched between the mounting bolts 44 and 48, the fastening of the split race rings 30 and 32 may be affected depending on conditions. The “conditions” mentioned here include the material of the inner race ring 14, the diameters of the mounting bolts 44, 48, the spacing between the fastening bolts 34 and the mounting bolts 44, 48 in the circumferential direction, the mounting bolts 44 relative to the fastening bolts 34, 48 layouts.

  More specifically, a stress is generated in a region around the corresponding female thread portion 32b in the split race ring 32 by the tightening torque of the mounting bolts 44 and 48. When the fastening bolt 34 is sandwiched between the mounting bolts 44 and 48, a region around the fastening bolt 34 in the inner race 14 may be displaced depending on conditions due to the stress generated by the fastening torque. Thereby, for example, the state of the fastening bolt 34 such as the distance between the fastening bolts 34 is changed, the fastening state of the split race rings 30 and 32 by the fastening bolt 34 is changed, and the split race rings 30 and 32 to the rolling element 16. The pressurization of the air pressure may vary greatly from the predetermined pressurization.

  Therefore, the fastening bolt 34 and the mounting bolt holes 46 and 50 (that is, the mounting bolts 44 and 48) are different in the radial position (Y-axis direction position) so that the fastening bolt 34 is not sandwiched between the mounting bolts 44 and 48. Is preferred. In particular, the mounting bolt holes 46 and 50 (that is, the mounting bolts 44 and 48) and the fastening bolt 34 are more preferably aligned in the radial direction. When aligned in the radial direction, the pressure (force applied to the rolling elements 16) can be balanced in the radial direction, which is more effective.

  Moreover, since the radial direction position of the fastening bolt 34 and the attachment bolts 44 and 48 is different, as a secondary effect, a plurality of fastening bolts 34 can be arranged at a small arrangement interval in the circumferential direction. That is, the split raceway rings 30 and 32 can be fastened to each other using many fastening bolts 34. As a result, the rigidity of the inner raceway ring 14 can be improved. Similarly, by disposing each of the plurality of mounting bolts 44 and 48 at a small arrangement interval in the circumferential direction, the outer members 40 and 42 and the inner race ring 14 can be more integrated and their rigidity can be improved. By improving the rigidity, noise generation from the rolling bearing device 10 is suppressed.

  As shown in FIGS. 1 and 2, the mounting bolt holes 46 and 50 (that is, the mounting bolts 44 and 48) are preferably provided at positions farther from the rolling element 16 than the fastening bolts 34. Thereby, it is suppressed that the part of the inner race 14 in contact with the rolling element 16 is displaced by the tightening torque of the mounting bolts 44 and 48. As a result, a predetermined pressure from the inner raceway 14 to the rolling element 16 is maintained even after the external members 40 and 42 are attached to the inner raceway 14 via the attachment bolts 44 and 48. When the mounting bolt holes 46 and 50 are sufficiently separated from the rolling element 16, the mounting bolt holes 46 and 50 may exist between the rolling element 16 and the fastening bolt 34.

  In this regard, as shown in FIG. 2, the mounting bolt holes 46 and 50 (that is, the mounting bolts 44 and 48) are arranged on the inner side in the radial direction (Y-axis direction) with respect to the fastening bolt 34. Further preferred. Thereby, it is further suppressed that the portion of the inner race 14 in contact with the rolling element 16 is displaced by the tightening torque of the mounting bolts 44 and 48.

  Further, as shown in FIG. 2, it engages with a female screw portion 32 b that engages with the male screw portions 44 c and 48 c of the mounting bolts 44 and 48, and with a male screw portion 34 c of the fastening bolt 34 that fastens the split race rings 30 and 32. The female threaded portion 32a is preferably formed in the same divided race ring 32.

  Thereby, the manufacturing cost of the rolling bearing device is reduced as compared with the case where the female screw portion of the fastening bolt hole and the female screw portion of the mounting bolt hole are formed in different split races.

  For example, in the case of the rolling bearing device 10 shown in FIG. 3, it is not necessary to form the female thread portions 32 a and 32 b only in the divided raceway ring 32 of the inner raceway ring 14 and to form the female thread portion in the split raceway ring 30. As a result, the threading process is shortened as compared with the case where the female thread portion engaging with the male thread portion 34c of the fastening bolt 34 is formed on the divided raceway ring 30 unlike this. For example, in a machine tool that performs machining on the split race 30, the tooling time for exchanging with a tap for threading is omitted. As a result, the manufacturing cost of the rolling bearing device 10 is reduced.

  Further, as shown in FIG. 2, it is preferable that the mounting bolt 44 for mounting the external member 40 on the split race 30 is shorter.

  Specifically, the mounting bolt 44 needs to pass through the divided race ring 30 so that the male thread portion 44c engages with the female thread portion 32b of the split race ring 32, and is therefore long. In consideration of the rigidity after fixing and integrating the external member 40 to the divided raceway ring 32, the mounting bolt 44 is preferably shorter.

  In order to shorten the mounting bolt 44, a part 32 c of the split race ring 32 protrudes toward the split race ring 30. Further, the convex part 32 c of the divided raceway ring 32 is annular, and the annular convex part 32 c is accommodated in an annular concave part 30 d formed in the split raceway ring 30. The through hole 30c of the mounting bolt hole 46 formed in the split race 30 communicates with the bottom of the recess 30d, and the screw 32b extends in the axial direction from the top of the projection 32c because it is formed in the split race 32. ing. That is, the female thread portion 32 b of the mounting bolt hole 46 through which the mounting bolt 44 is inserted is formed only in the divided raceway ring 32, but a part thereof is located on the inner side of the divided raceway ring 30. Thereby, the male threaded portion 44 c of the mounting bolt 44 can be engaged with the female threaded portion 32 b of the divided raceway ring 32 without greatly passing through the divided raceway ring 30. As a result, the mounting bolt 44 can be shortened, the external member 40 and the divided raceway ring 32 are more integrated to improve the rigidity, and the generation of noise from the rolling bearing device 10 is suppressed due to the improved rigidity. .

  According to the present embodiment as described above, in the axial direction of the inner race 14 of the rolling bearing device 10 configured by fastening a plurality of parts while suppressing a change in the pressure applied to the rolling element 16. External members 40, 42 can be attached to the ends. Thereby, noise generation from the rolling bearing device 10 can be suppressed.

  Although the present invention has been described with reference to the above-described embodiments, the present invention is not limited to the above-described embodiments.

  For example, in the case of the above-described embodiment, the bearing ring that is configured by fastening a plurality of parts and to which an external member is attached is an inner bearing ring, but the embodiment of the present invention is not limited thereto. For example, the outer race may be configured by fastening a plurality of parts in the axial direction, and an external member may be attached to the axial end of the outer race.

  Moreover, in the case of the above-mentioned embodiment, although a rolling element is spherical, embodiment of this invention is not restricted to this. For example, the rolling element may have a roller shape.

  Further, in the case of the above-described embodiment, as shown in FIG. 2, the mounting bolts 44 and 48 are engaged with the common female thread portion 32 b formed on the divided raceway ring 32, so that the axial direction (X-axis direction) Opposite to. However, the embodiment of the present invention is not limited to this. For example, in another embodiment of the present invention, one mounting bolt and the other mounting bolt do not face each other in the axial direction, and a separate female thread portion that engages with each mounting bolt has only one split raceway. It is formed.

  Further, when viewed in the entire circumferential direction, the mounting bolt holes and the fastening bolt holes are not necessarily the same in number. Furthermore, the positional relationship between the mounting bolt hole and the fastening bolt need not be uniform over the entire circumference. That is, it is more preferable that these positional relationships are uniform over the entire circumference, but the positional relationship between one or a part of the mounting bolt holes and the fastening bolts is the other mounting bolt holes and the fastening bolts. If the positional relationship is uniform over the entire circumference, the positional relationship between the mounting bolt holes and the fastening bolts is not necessarily the same as long as the positional relationship is uniform over the entire circumference. It need not be uniform over the circumference.

  The inventor provides the accompanying drawings and the following description in order for those skilled in the art to fully understand the present disclosure, and is intended to limit the subject matter described in the claims. is not.

  The present invention is not limited to a rolling bearing device used in a CT scanning device, but can be applied to a rolling bearing device in which a raceway ring is configured by fastening a plurality of parts, and pressure is applied to a rolling element. is there.

10 Rolling bearing device 12 Second raceway (outer raceway)
14 First race (inner race)
16 Rolling elements 30 Second split race ring (split race ring)
32 First split race ring (split race ring)
32b Female thread portion 34 Fastening bolt 40 Second external member (external member)
42 First external member (external member)
44 Second mounting bolt (mounting bolt)
46 Second mounting bolt hole (Mounting bolt hole)
48 First mounting bolt (mounting bolt)
50 First mounting bolt hole (Mounting bolt hole)

Claims (4)

A first race ring;
A second race,
A plurality of rolling elements arranged in a circumferential direction in an annular space between the first raceway and the second raceway,
A first split race ring disposed on one side in the axial direction; a second split race ring disposed on the other side in the axial direction; and the first split race ring; A plurality of fastening bolts for fastening the second split race ring in the axial direction;
The plurality of first bearing rings are for a plurality of first mounting bolts for axially mounting a first external member present on one side in the axial direction on the first split bearing ring side. A plurality of second mounting bolts for axially mounting a first mounting bolt hole and a second external member present on the other axial side on the second split race ring side. A second mounting bolt hole,
Both the female thread portion of the first mounting bolt hole that engages with the first mounting bolt and the female thread portion of the second mounting bolt hole that engages with the second mounting bolt are the first thread. A rolling bearing device formed on a split race. The first split race ring and the second split race ring are fastened in the axial direction by the plurality of fastening bolts arranged in the circumferential direction,
The plurality of first mounting bolt holes are formed in a state aligned in the circumferential direction at one end in the axial direction of the first track ring,
The plurality of second mounting bolt holes are formed in a state aligned in the circumferential direction at the other end in the axial direction of the first track ring,
The rolling bearing device according to claim 1, wherein the first and second mounting bolt holes are different in position in the radial direction from positions in the radial direction of the fastening bolts.   The rolling bearing device according to claim 2, wherein the first and second mounting bolt holes and the fastening bolt are arranged in a radial direction. The first split race ring includes a convex portion that protrudes toward the second split race ring,
The second split race ring has a recess that can accommodate the convex portion of the first split race ring,
The rolling bearing device according to any one of claims 1 to 3, wherein a female thread portion of the second mounting bolt hole is formed on a convex portion of the first divided raceway ring.

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