JP2016145611A - Split bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To stably maintain a seal function by widening a width of a slide face sliding with a seal member of an inner ring without enlarging a width dimension of a split bearing having the seal member.SOLUTION: In a split bearing which has an inner ring main body 8 having an external peripheral raceway surface 2a of an inner ring 2, and a slide face 2b sliding with a seal member 7, and in which a pair of fastening rings 9 for fastening an external periphery of an end of the inner ring main body 8 in an axial direction are split into two pieces in peripheral directions, a circular hole (fastening operation recess) 10b is formed at an end face of a half body 10 of one of the fastening rings 9, an eccentric cam 13 fit into the circular hole 10b is engaged with a head 12a of a cam lock screw 12 which is screwed into the other half body 11, the slide face 2b sliding with the seal member 7 of the inner ring 2 can be formed with a wide width at the external periphery of the end of the inner ring 2 in the axial direction without enlarging a width dimension of the bearing as a whole by entirely integrating the inner ring 2, and a seal function of the seal member 7 can be stably maintained.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a split bearing used for steel equipment such as a continuous casting machine and a rolling mill, a crankshaft, and the like.

  Rollers that transport steel materials with large weight and width in the longitudinal direction in steel facilities such as continuous casting machines and rolling mills are subjected to a large load in the direction perpendicular to the axial direction. Is also supported by a bearing to suppress deflection at the axially central portion. Since the bearing provided in the central portion in the axial direction is difficult to assemble in the axial direction, a split bearing in which components such as an inner ring and a housing are divided into a plurality in the circumferential direction is used. This split bearing is widely used as a bearing for supporting a shaft member (for example, a crank pin or a journal portion that connects adjacent crank arms of a crankshaft) that cannot be assembled into an integral bearing, other than steel facilities. .

  The split bearing includes an inner ring, an outer ring, a rolling element such as a plurality of cylindrical rollers arranged between the outer raceway surface of the inner ring and the inner raceway surface of the outer ring, a housing for fixing the outer ring, and a rolling element. In many cases, each component excluding the rolling elements is divided into two parts in the circumferential direction and integrated with bolts or the like when assembled to the shaft member. In addition, in a split bearing used in an environment where water, dust, or the like scatters, a pair of seal members attached to the housing are slidably contacted with sliding surfaces formed on the outer periphery of both ends of the inner ring in the axial direction. In order to prevent foreign matter from entering the bearing, there are some.

  By the way, such a split bearing is usually provided with a counterbore (clamping operation recess) for performing a tightening operation of a fastening bolt that integrates the inner ring on the outer peripheral surface of both axial ends of the inner ring. Therefore, when the sealing member is provided, the sliding surface of the inner ring is formed in a portion excluding the counterbore part on the outer peripheral surface of the inner ring. For this reason, when supporting the shaft member of the equipment which becomes high temperature with the split bearing having the seal member, the inner ring of the split bearing is relatively axially moved with respect to the shaft member due to the axial thermal expansion of the shaft member. By moving in the direction, the seal lip at the tip of the seal member is detached from the sliding surface of the inner ring and applied to the counterbore, the original sealing function of the seal member is impaired, and foreign matters such as water enter the bearing, The bearing life may be shortened.

  The split bearing having the seal member includes an inner ring including an inner ring body having an outer circumferential raceway surface and a pair of tightening rings for tightening outer circumferences of both end portions in the axial direction of the inner ring body. Some of these surfaces have a counterbore for tightening operation of the fastening bolt and a sliding surface for the seal member. However, even with a split bearing of this configuration, the axial expansion of the shaft member when used at high temperatures. As a result, the seal lip of the seal member is detached from the sliding surface of the inner ring (clamping ring), the sealing function is impaired, and the bearing life may be shortened.

  On the other hand, as in the split bearing described in Patent Document 1, for example, both ends in the axial direction of the inner ring are extended to increase the width of the sliding surface with the seal member, and the inner ring is relative to the shaft member. If the seal lip of the seal member is not removed from the sliding surface even if it moves somewhat in the axial direction, the seal function is maintained even at high temperatures, and the bearing life can be prevented from being shortened.

Japanese Patent Laid-Open No. 9-112541

  However, in the split bearing in which the axial end portion of the inner ring is extended as in Patent Document 1, the overall width of the bearing is increased, which is a cause of hindering the downsizing of equipment in which the bearing is incorporated. It is considered that it is difficult to assemble the shaft member.

  On the other hand, there are those shown in FIGS. 10 to 12 as split bearings in which the width of the sliding surface of the inner ring is increased without changing the overall width of the bearing. As shown in FIGS. 10 and 11, the split bearing 51 supports a journal portion J that connects adjacent crank arms A of the crankshaft C. The split bearing 51 supports the outer raceway surface 52 a of the inner ring 52 and the outer ring 53. A plurality of cylindrical rollers (rolling elements) 55 movably held by the cage 54 are arranged between the inner circumferential raceway surface 53 a and a pair of seal members 57 are attached to a housing 56 that fixes the outer ring 53. ing.

  The housing 56 includes a main body portion 56a and a pair of seal attachment portions 56b fixed to both end surfaces of the main body portion 56a, and a seal member 57 is fitted into an annular groove formed on the inner periphery of each seal attachment portion 56b. ing. Each seal member 57 has two seal lips 57a and 57b on the inner periphery thereof, and is in sliding contact with the slide surfaces 52b formed on the outer periphery of both end portions in the axial direction of the inner ring 52 by both seal lips 57a and 57b. Yes.

  Each component of the split bearing 51 other than the cylindrical roller 55 is divided into two parts in the circumferential direction, and is integrated with a bolt or the like when assembled to the journal portion J. The integrated structure of the inner ring 52 will be described below.

  The inner ring 52 has an inner ring main body 58 having an outer raceway surface 52a, a pair of tightening rings 59 for tightening the outer circumferences of both ends in the axial direction of the inner ring main body 58, and a sliding surface 52b for the seal member 57. The inner ring main body 58, each fastening wheel 59, and each sliding wheel 60 are each divided into two in the circumferential direction.

  Then, as shown in FIGS. 11 and 12, a counterbore (a recess for tightening operation) opened on the outer peripheral surface of one half of the tightening wheel 59 and the sliding wheel 60 on the joint surface with the other half. 59a and 60a are provided, and with the inner ring body 58 assembled to the journal portion J, the clamping rings 59 are assembled to the outer periphery of both axial ends thereof, and the counterbore 59a of one half of each clamping ring 59 is provided. After the fastening bolt 61 inserted into the other half is screwed, the sliding ring 60 is assembled to the outer periphery of each fastening ring 59, and the fastening bolt 62 inserted into the counterbore 60a of one half of each sliding ring 60 is attached. By screwing into the other half, the entire inner ring 52 is integrated.

  Here, the fastening bolt 61 for the fastening ring 59 is of a thickness that can secure the fastening strength necessary to maintain the integrated state of the inner ring main body 58 and the fastening ring 59. On the other hand, the fastening bolt 62 for the sliding wheel 60 may be any bolt as long as the sliding wheel 60 can secure a fastening strength sufficient to fasten the outer periphery of the fastening wheel 59. A small diameter is used. Accordingly, the counterbore 60a of the sliding wheel 60 is formed smaller than the counterbore 59a of the tightening wheel 59, and the sliding surfaces 52b of the inner ring 52 formed on both sides of the counterbore 60a on the outer peripheral surface of the sliding wheel 60 are sliding wheels. The width dimension can be made wider than the case where the outer peripheral surface of the fastening ring 59 is formed on both sides of the counterbore 59a in the absence of 60.

  As described above, the split bearing 51 can increase the width of the sliding surface of the inner ring to some extent without changing the width dimension of the entire bearing as compared with the split bearing having no sliding ring. However, since there is a limit to reducing the size of the counterbore 60a of the sliding wheel 60 by reducing the diameter of the fastening bolt 62 for the sliding wheel 60, the amount of increase in the width dimension of the sliding surface 52b of the inner ring 52 is small, so In some cases, shortening of the bearing life due to a decrease in the sealing function cannot be sufficiently prevented.

  Further, in this split bearing 51, the two seal lips 57a, 57b of the seal member 57 are in sliding contact with both sides of the counterbore 60a portion of the outer peripheral surface of the sliding wheel 60, so the shape thereof is limited to some extent. In other words, there is a problem that the dimensional accuracy becomes strict and the production takes time.

  Therefore, the present invention increases the width of the sliding surface of the inner ring with the seal member without increasing the width of the split bearing having the seal member so that the sealing function is stably maintained. Is an issue.

  In order to solve the above-described problems, the present invention provides an inner ring that is divided into a plurality of parts in the circumferential direction and integrated with fastening bolts, an outer ring that is arranged radially outside the inner ring, and an outer raceway surface of the inner ring. And a plurality of rolling elements that roll between the inner raceway surface of the outer ring, a housing to which the outer ring is fixed, and a slide that is attached to the housing and formed on the outer circumference of the axial end of the inner ring In the split bearing having a seal member that is in sliding contact with the surface, a configuration is adopted in which a recess for tightening operation for tightening the fastening bolt is provided on the end face side of the inner ring. Here, the “end surface side of the inner ring” includes the end surface of the inner ring (the same applies hereinafter).

  That is, by providing a tightening operation recess for tightening the fastening bolt on the end face side of the inner ring divided into a plurality in the circumferential direction, a tightening operation recess is provided on the outer periphery of the axial end of the inner ring. The sliding surface of the inner ring with the sealing member can be formed with a wider width on the outer periphery of the axial end of the inner ring without increasing the overall width of the bearing.

  Here, the inner ring includes an inner ring main body having the outer peripheral raceway surface, and a tightening ring having the sliding surface and a concave portion for tightening operation and tightening the outer periphery of the axial end of the inner ring main body. Or an inner ring body having the outer raceway surface, a tightening ring for tightening the outer periphery of the axial end of the inner ring body, the sliding surface and a tightening operation recess, and an outer periphery of the tightening ring It can also consist of a sliding wheel which tightens.

  A cam lock screw can be adopted as the fastening bolt. In that case, the insertion hole into which one of the two members coupled to each other by the cam lock screw is inserted with the head of the cam lock screw screwed into the other member and the tightening operation A cam member that is provided so as to communicate with each other and is slidably fitted in the recess for tightening operation may be engaged with the head of the cam lock screw.

  Further, as the fastening bolt, a screw with a bevel gear having a bevel gear at the head may be employed. In that case, one of the two members coupled to each other with the screw with a bevel gear is provided with the concave portion for tightening operation, and the screw with bevel gear inserted into the concave portion for tightening operation is What is necessary is just to screw in the other member of said two members with the fastening operation screw which has the bevel gear part meshing | engaged with the bevel gear of a head.

  It is desirable that the sliding surface of the inner ring be plated.

  The above-described split bearing of the present invention is particularly effectively used in a steel facility or a crankshaft.

  As described above, the split bearing of the present invention is provided with a recess for tightening operation for tightening a fastening bolt that integrates the inner ring on the end face side of the inner ring divided into a plurality in the circumferential direction. Therefore, the sliding surface of the inner ring with the sealing member of the inner ring can be adjusted without increasing the overall width of the bearing compared to the conventional one in which the outer periphery of the axial end of the inner ring is provided with a recess for tightening operation. It can be formed with a wide width on the outer periphery of the direction end. Therefore, even if the inner ring moves slightly in the axial direction relative to the shaft member due to thermal expansion of the shaft member to which the split bearing is assembled, the seal lip of the seal member does not come off from the sliding surface of the inner ring. In addition, the sealing function of the sealing member is stably maintained, and there is no possibility of shortening the service life.

  In addition, since the sliding surface of the inner ring is formed continuously in the width direction, the sealing member has a seal lip shape as compared with the sealing member that is in sliding contact with the narrow sliding surfaces on both sides of the conventional concave portion for tightening operation. The degree of freedom is increased, and the dimensional accuracy is also loosened, making it easy to manufacture.

Longitudinal front view of the split bearing of the first embodiment in use Fig. 1 is an enlarged vertical front view of a main part excluding the housing of the split bearing of Fig. 1. Right side view of FIG. FIGS. 2A to 2C are explanatory diagrams of procedures for integrating the inner ring in a cross section taken along line IV-IV in FIG. The longitudinal front view of the principal part except the housing of the split bearing of 2nd Embodiment a is a right side view of the main part of the split bearing of FIG. 5, and b is a cross-sectional view taken along line VI-VI of a. FIGS. 6A to 6C are partially cutaway side views for explaining the inner ring integration procedure corresponding to FIG. Longitudinal front view of the main part of the split bearing of the third embodiment Longitudinal side view of main part of split bearing of fourth embodiment Longitudinal front view of a conventional split bearing in use Fig. 10 is an enlarged vertical front view of a main part excluding the housing of the split bearing. Sectional drawing along the XII-XII line of FIG.

  Hereinafter, embodiments of the present invention will be described with reference to FIGS. 1 to 9.

  1 to 4 show a first embodiment. As shown in FIGS. 1 and 2, the split bearing 1 supports a journal portion J that connects adjacent crank arms A of the crankshaft C, and includes an inner ring 2 attached to the outer periphery of the journal portion J, and The outer ring 3 disposed radially outside the inner ring 2, the plurality of cylindrical rollers (rolling elements) 4 that roll between the outer raceway surface 2a of the inner ring 2 and the inner raceway surface 3a of the outer ring 3, and cylindrical rollers 4 is provided with a retainer 5 that holds 4 in a rotatable manner, a housing 6 to which the outer ring 3 is fixed, and a pair of seal members 7 attached to the housing 6. The cylindrical roller can be replaced with another rolling element such as a ball.

  The housing 6 includes a main body portion 6a and a pair of seal attachment portions 6b fixed to both end faces of the main body portion 6a, and the seal member 7 is fitted into an annular groove formed on the inner periphery of each seal attachment portion 6b. ing. Each seal member 7 has two seal lips 7a and 7b on the inner circumference thereof, and is in sliding contact with the slide surfaces 2b formed on the outer circumferences of both end portions in the axial direction of the inner ring 2 with both seal lips 7a and 7b. Yes.

  Each component (inner ring 2, outer ring 3, cage 5, housing 6 and seal member 7) of the split bearing 1 except for the cylindrical roller 4 is divided into two parts in the circumferential direction. Etc. to be integrated. The integrated structure of the inner ring 2 will be described below.

  The inner ring 2 includes an inner ring body 8 having an outer raceway surface 2a, and a pair of tightening rings 9 for tightening the outer periphery of both ends in the axial direction of the inner ring body 8. The inner ring body 8 and each tightening ring 9 are respectively Divided into two in the circumferential direction. The inner ring main body 8 is provided with annular grooves 8a on both sides of the outer raceway surface 2a, and the fastening ring 9 is fitted into each annular groove 8a. In addition, a plating process is performed on a portion other than the chamfered portion of the outer peripheral surface of each tightening ring 9, and the plated surface is a sliding surface 2 b that slides on the seal lips 7 a and 7 b of the seal member 7. It has become.

  As shown in FIGS. 2 and 3, the tightening wheel 9 is obtained by connecting two halves 10 and 11 with a cam lock screw 12 serving as a fastening bolt and an eccentric cam (cam member) 13. An elastic sheet member 14 is interposed between the two halves 10 and 11 to enhance the adhesion between the halves 10 and 11. One half body 10 has an opening at the joint surface with the other half body 11, an insertion hole 10 a into which the head 12 a side portion of the cam lock screw 12 is inserted, an opening at the outer end face, and an eccentric cam 13. Circular holes (tightening operation recesses) 10b that are slidably fitted are provided so as to communicate with each other. Further, the other half 11 is provided with a screw hole 11 a into which the tip end portion of the cam lock screw 12 is screwed into the joint surface with the other half 10.

  When integrating the inner ring 2, first, as shown in FIG. 4 (a), with the two outer halves of the inner ring body 8 sandwiching the outer periphery of the journal portion J of the crankshaft C, The head 12a side of the cam lock screw 12 screwed into the screw hole 11a of the other half body 11 of the fastening ring 9 in advance while being fitted in each annular groove 8a of the inner ring body 8 so that the two half bodies 10, 11 abut each other. The part is inserted into the insertion hole 10 a of one half 10. Then, as shown in FIG. 4 (b), by rotating the eccentric cam 13 fitted in the circular hole 10b of one half body 10, as shown in FIG. 4 (c), the eccentric cam 13 and the cam lock The two halves 10 and 11 may be coupled by engaging the head 12 a of the screw 12, and the two halves of the inner ring main body 8 may be tightened.

  The split bearing 1 has the above-described configuration, and a circular hole 10b is provided in the end surface of one half body 10 of the tightening ring 9 constituting the inner ring 2, and the eccentric cam 13 fitted in the circular hole 10b is connected to the other end. Since the inner ring 2 is integrated as a whole by engaging with the head 12a of the cam lock screw 12 screwed into the half body 11, the inner ring is more than the conventional split bearing 51 shown in FIGS. The sliding surface 2b with the sealing member 7 of 2 (clamping ring 9) can be formed with a wide width.

  Therefore, even if the inner ring 2 moves slightly in the axial direction relative to the journal part J due to thermal expansion of the journal part J of the crankshaft C, the seal lips 7a and 7b of the seal member 7 slide on the inner ring 2. It does not come off from the surface 2b, the sealing function of the sealing member 7 is maintained, and it can be used stably for a long time.

  Further, since the overall width of the bearing is the same as that of the conventional split bearing 51, it can be easily assembled to the existing crankshaft C, and the crankshaft C and the equipment in which the crankshaft C is incorporated are not increased. Compared to the conventional split bearing 51, the number of main parts can be reduced by the absence of the sliding wheel 60.

  Furthermore, since the sliding surface 2b of the inner ring 2 is formed continuously in the width direction, the sealing lips 7a, 7b of the sealing member 7 have a greater degree of freedom in shape than that of the conventional split bearing 51. Therefore, there is an advantage that the dimensional accuracy is also loosened and the manufacture becomes easy.

  5 to 7 show a second embodiment. In this embodiment, the integrated structure of the inner ring 2 of the first embodiment is changed, and a bevel gear screw 15 is employed as a fastening bolt for connecting the two halves 10 and 11 of the fastening ring 9. . In addition, the same code | symbol is attached | subjected to the member of the same function as 1st Embodiment, and description is abbreviate | omitted (same also about 3rd, 4th embodiment mentioned later).

  As shown in FIGS. 5 and 6 (a) and 6 (b), one half body 10 of the fastening ring 9 of the second embodiment has an opening at the joint surface with the other half body 11, and an umbrella. An insertion hole 10c into which the geared screw 15 is inserted, and a rectangular hole (clamping operation concave portion) 10d that opens to the outer end face and is inserted in a posture in which the bevel geared screw 15 is directed toward the other half body 11. Are in communication with each other.

  And the counterbore 10d of one half 10 is provided with counterbore on each edge, and is inserted into the inner ring 2 inner peripheral side and outer peripheral side sidewalls from the longitudinal center to the insertion hole 10c side. A protrusion 10e extending in parallel with the hole 10c is provided. As a result, the bevel gear portion formed at the tip of the tightening operation screw 16 for screwing the bevel gear-attached screw 15 is slidably engaged with the counterbore portion of the rectangular hole 10d. 16a meshes with the bevel gear 15a at the head of the screw 15 with the bevel gear, and is guided by the ridge 10e at the neck portion to move in parallel. Further, the other half body 11 is provided with a screw hole 11 b into which the tip side portion of the bevel gear-attached screw 15 is screwed into the joint surface with the other half body 10.

  When the inner ring 2 is integrated, first, as in the first embodiment, the outer periphery of the journal portion J of the crankshaft C is sandwiched between the two halves of the inner ring main body 8 as shown in FIG. As described above, the two halves 10 and 11 of the tightening ring 9 are fitted into the respective annular grooves 8a of the inner ring main body 8, and a screw with a bevel gear is inserted into the rectangular hole 10d of one half 10 of the tightening ring 9. 15 is inserted, and the tip is inserted into the insertion hole 10c communicating with the rectangular hole 10d. Then, as shown in FIG. 7B, the tightening operation screw 16 is fitted into the side opposite to the insertion hole 10c of the rectangular hole 10d (the side without the protrusion 10e), and the bevel gear portion 16a is attached to the bevel gear portion 16a. After meshing with the bevel gear 15a of the geared screw 15, the screw 15 with bevel gear is moved in parallel to the insertion hole 10c along the protrusion 10e while rotating the tightening operation screw 16, and the screw 15 with bevel gear is moved to the other half. By screwing into the screw hole 11b of the body 11, both halves 10 and 11 may be coupled and the two halves of the inner ring main body 8 may be tightened as shown in FIG. When the inner ring 2 is integrated, the protrusion 10e of the rectangular hole 10d of the tightening ring 9 prevents the tightening operation screw 16 from coming off in the axial direction. There is no risk of falling off.

  In the second embodiment as well, as in the first embodiment, the fastening bolt for fastening the fastening bolt for integrating the inner ring 2 to the end surface of one half body 10 of the inner ring 2 (clamping ring 9) is used. Since the recess is provided, the same effect as the first embodiment can be obtained.

  In the first and second embodiments described above, the split bearing including the inner ring including the inner ring main body and the pair of tightening rings has been described. However, the present invention is a split bearing in which the configuration of the inner ring is different from those of each of the embodiments. It can also be applied to.

  For example, the split bearing of the third embodiment shown in FIG. 8 has a sliding surface 2b with the outer raceway surface 2a and the seal member 7 instead of the inner ring 2 of the first embodiment, and is divided into two in the circumferential direction. The inner ring 2 consisting only of the inner ring main body 8 is incorporated, and the same integrated structure as that of the first embodiment is adopted for the inner ring 2.

  That is, in the third embodiment, circular holes (clamping recesses) 2c and insertion holes (not shown) into which the cam lock screws 12 are inserted into both end faces of one half of the inner ring 2 (inner ring main body 8). Are provided so as to communicate with each other, and a screw hole (not shown) into which the tip side portion of the cam lock screw 12 is screwed is provided at both ends of the other half, and the eccentric cam fitted into the circular hole 2c of one half The inner ring 2 is integrated by engaging 13 with the head of a cam lock screw 12 screwed into the other half.

  On the other hand, the split bearing of the fourth embodiment shown in FIG. 9 includes an inner ring body 8 having an outer raceway surface (not shown) instead of the inner ring 2 of the first embodiment, and outer circumferences of axial end portions of the inner ring body 8. The inner ring 2 includes a pair of tightening wheels 9 for tightening and a sliding surface 2b between the seal member 7 and a pair of sliding wheels 17 for tightening the outer periphery of the tightening wheel 9. The inner ring 2 includes an inner ring body 8, each fastening ring 9, and each sliding ring 17 divided into two in the circumferential direction. The inner ring body 8 and each fastening ring 9 are shown in FIG. 10 to FIG. They are integrated by the same means as the split bearing 51, and the same integrated structure as that of the first embodiment is adopted for each sliding wheel 17.

  That is, in the fourth embodiment, a circular hole (clamping operation recess) 17a and an insertion hole 17b into which the cam lock screw 12 is inserted are provided on the end face of one half of each sliding wheel 17 so as to communicate with each other. The other half is provided with a screw hole 17c into which the tip side portion of the cam lock screw 12 is screwed. Then, the two halves of the fastening ring 9 are fitted into the annular grooves 8a provided on both sides of the outer raceway surface of the inner ring body 8 in a state where the halves are brought into contact with each other. After the bolt 18 inserted into the half-bore 9a is screwed into the other half, the sliding wheel 17 is assembled to the outer periphery of each tightening wheel 9, and the circular hole 17a of one half of each sliding wheel 17 is assembled. The entire inner ring 2 is integrated by engaging the fitted eccentric cam 13 with the head 12a of the cam lock screw 12 screwed into the other half.

  Since the sealing member of the present invention has a large degree of freedom of shape as described above, it is not limited to the shape of each embodiment (same as the conventional one), but also has a shape with higher sealing performance and a shape that is easy to manufacture Can be adopted. Moreover, parts other than a rolling element do not necessarily need to be divided into two like each embodiment, and may divide into three or more.

  Further, the present invention is not limited to the split bearing that supports the journal portion of the crankshaft as in the embodiment. For example, the shaft in a steel plant such as one that supports the crankpin of the crankshaft or a continuous casting machine or a rolling mill. It can be effectively applied to a split bearing having a seal member that supports the central portion of the member.

DESCRIPTION OF SYMBOLS 1 Split bearing 2 Inner ring 2a Outer raceway surface 2b Sliding surface 3 Outer ring 3a Inner raceway surface 4 Cylindrical roller (rolling element)
5 Cage 6 Housing 7 Seal member 7a, 7b Seal lip 8 Inner ring body 9 Clamping ring 10 Half body 10a, 10c Insertion hole 10b Circular hole (recess for tightening operation)
10d rectangular hole (recess for tightening operation)
10e ridge 11 other half 11a, 11b (clamping ring) screw hole 12 cam lock screw (fastening bolt)
13 Eccentric cam (cam member)
15 Screw with bevel gear (fastening bolt)
15a Bevel gear 16 Tightening operation screw 16a Bevel gear portion 17 Sliding wheel 17a Circular hole (recess for tightening operation)
17b Insertion hole 17c Screw hole C Crankshaft A Crank arm J Journal part

Claims (7)

  Rolling between an inner ring that is divided into a plurality in the circumferential direction and integrated with fastening bolts, an outer ring that is arranged radially outward of the inner ring, and an outer raceway surface of the inner ring and an inner raceway surface of the outer ring A split bearing comprising: a plurality of rolling elements; a housing to which the outer ring is fixed; and a seal member attached to the housing and in sliding contact with a sliding surface formed on an outer periphery of an axial end of the inner ring. A split bearing having a recess for tightening operation for tightening the fastening bolt on the end face side of the inner ring.   The inner ring includes an inner ring body having the outer raceway surface, and a tightening ring having the sliding surface and a tightening operation recess and tightening the outer periphery of the axial end of the inner ring body. The split bearing according to claim 1.   The inner ring includes an inner ring body having the outer raceway surface, a tightening ring for tightening an outer periphery of an axial end portion of the inner ring body, the sliding surface and a recess for tightening operation, The split bearing according to claim 1, comprising a sliding wheel for tightening an outer periphery.   The fastening bolt is a cam lock screw, and an insertion hole into which one of the two members coupled to each other by the cam lock screw is inserted with the head of the cam lock screw screwed into the other member. The clamp operation recess is provided so as to communicate with each other, and a cam member slidably fitted in the tightening operation recess is engaged with a head of the cam lock screw. The split bearing according to any one of 1 to 3.   The fastening bolt is a screw with a bevel gear having a bevel gear at the head, and the tightening operation recess is provided in one of two members coupled to each other by the screw with the bevel gear. The screw with the bevel gear inserted into the recess for operation is screwed into the other member of the two members by a tightening operation screw having a bevel gear portion meshing with the bevel gear at the head. The split bearing according to any one of claims 1 to 3.   The split bearing according to any one of claims 1 to 5, wherein the sliding surface of the inner ring is plated.   The split bearing according to any one of claims 1 to 6, wherein the split bearing is used in a steel facility or a crankshaft.

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