JP5532901B2 - Split type rolling bearing - Google Patents

Description

  The present invention relates to a split type rolling bearing in which an outer ring member is configured by both outer ring divided bodies divided into two in the circumferential direction.

In a split type rolling bearing for rotatably supporting a crankshaft of an internal combustion engine of an automobile, a ship, etc. on both split housing bodies of a housing, the outer ring member is constituted by a double outer ring split body divided into two in the circumferential direction. A structure that is assembled to both divided housing bodies constituting the housing is known.
In such a split type rolling bearing, due to an assembly error due to fastening of bolts or the like of both split housing bodies, a slight misalignment may occur on the split surfaces of both outer ring split bodies together with these split housing bodies. .
In this case, a step is generated at the joint portion of the split raceway surfaces of both outer ring split bodies, so that the rolling element may collide with the edge portion of the step, leading to vibration, noise, damage, and the like. Further, when the step is large, it is assumed that rotation failure occurs.
For this reason, for example, as shown in FIG. 6, arc-shaped relief surfaces 125 and 135 are formed on the divided raceway surfaces 122 and 132 of both outer ring divided bodies 121 and 131 constituting the outer ring member 120. A split type rolling bearing is known.
For example, Patent Document 1 discloses a split-type rolling bearing in which arc-shaped flank surfaces are formed on the split raceway surfaces of both outer ring members of the outer ring member.

JP 2007-2914 A

By the way, in the conventional structure shown in FIG. 6, when the bearing rotates, the rolling element 115 causes a step generated between the divided surfaces 123 and 133 of the outer ring divided members 121 and 131 constituting the outer ring member 120. When passing, it is possible to prevent the rolling surfaces 115 from colliding with the edge E of the step by the flank surfaces 125 and 135.
However, when the rolling elements 115 that have passed through the steps of the respective split surfaces 123 and 133 reach the joint point P ′ between the split raceway surface 122 and the flank surface 125 of one outer ring split body 121, the joint point P ′ is reached. There is a risk of causing vibration, abnormal noise, damage, etc. by collision.

  In view of the above problems, an object of the present invention is a division that can alleviate vibration, noise, damage, etc. caused by a step generated between the divided surfaces of both outer ring divided bodies constituting the outer ring member. It is to provide a rolling bearing.

In order to solve the above-mentioned problem, the split type rolling bearing according to claim 1 of the present invention is a split type rolling bearing constituted by both outer ring divided bodies in which the outer ring member is divided into two in the circumferential direction,
The split raceway surfaces of the outer ring divided bodies are formed with first flank surfaces that are matched with the split surfaces of the outer ring split bodies to form a curved or arcuate shape,
Between the first flank and the divided raceway surface, a second flank that forms a curved surface or an arc surface that is deeper on the side connected to the first flank surface and becomes shallower as it approaches the divided raceway surface. Formed ,
The first flank has a center on a line connecting the split surface of the outer ring split body and the bearing raceway center and is formed in an arc shape with a smaller radius of curvature than the split raceway surface,
The second flank is formed in an arc shape with a radius of curvature having a center on a line connecting a junction between the second flank and the first flank and the bearing raceway center. And

According to the above configuration, when the rolling element passes through the step generated between the split surfaces of the outer ring divided members constituting the outer ring member during the rotation of the bearing, the rolling element collides with the edge of the step. It can be suppressed by the first flank.
In addition, the rolling elements that have passed through the first flank face are guided by the second flank face and roll toward the split raceway surface of one outer ring split body. For this reason, it is possible to satisfactorily suppress vibration, abnormal noise, damage, and the like caused by the steps generated between the split surfaces of the outer ring divided bodies.
As a result, it is possible to provide a split type rolling bearing excellent in quietness and durability.

The first relief surface is formed on the outer ring division bodies of the divided surface and the arc-shaped small radius of curvature than the bearing raceway center and and dividing the raceway surface has a center line connecting a second clearance surfaces, that are formed into an arc shape with a radius of curvature having a center on the line connecting the junction point and the bearing raceway center between the second flank of the first flank.

  According to the said structure, the 1st, 2nd flank of an outer ring division body can be grind | polished easily and accurately with a rotary grindstone.

The split rolling bearing according to claim 2 is the split rolling bearing according to claim 1 ,
A first flank angle formed by the tangent line of the split raceway surface and the tangent line of the first flank surface from the intersection of the split raceway surface and the first flank surface is defined as θ, and the split raceway surface and the second flank surface are When the second relief angle formed by the tangent line of the split raceway surface and the tangent line of the second flank from the intersection of
It is characterized in that it is set to have a relation of “θ> β”.

  According to the above configuration, the first clearance angle θ and the second clearance angle β are set to have a relationship of “θ> β”, which is effective in suppressing vibration, abnormal noise, damage, and the like. large.

It is a cross-sectional view which shows the state which assembled | attached the division | segmentation type rolling bearing which concerns on Example 1 of this invention to the housing. It is explanatory drawing which similarly shows the circular arc center of the 1st, 2nd flank of both outer ring | wheel division bodies. It is explanatory drawing which similarly shows flank angles (theta) and (beta) of the 1st, 2nd flank. Similarly, it is an explanatory view showing a state in which a level difference occurs due to a positional deviation by a deviation amount δ between the split surfaces of both outer ring split bodies. It is explanatory drawing which shows rolling of the rolling element at the time of bearing rotation in the state which the level | step difference generate | occur | produced in the division surface of both outer ring | wheel division bodies similarly. It is explanatory drawing which shows the rolling state of the rolling element at the time of the bearing rotation of the conventional division | segmentation type rolling bearing.

  The best mode for carrying out the present invention will be described in accordance with an embodiment.

A first embodiment of the present invention will be described with reference to FIGS.
As shown in FIG. 1, a split rolling bearing 10 for rotatably supporting a crankshaft 1 of an internal combustion engine such as an automobile or a ship on both split housing bodies 6 and 8 of a housing 5 is an outer peripheral surface of the crankshaft 1. As an inner ring raceway surface 2, an outer ring member 20 disposed on the outer periphery of the inner ring raceway surface 2 with an annular space, a plurality of rolling elements (rollers) 15, and a cage 16.
That is, semi-arc-shaped bearing assembly recesses 7 and 9 that are divided into two in the circumferential direction are formed on the split surfaces of the split housing bodies 6 and 8 of the housing 5, respectively. The divided housing body 8 is fastened by the bolt 4.

The outer ring member 20 includes two outer ring divided bodies 21 and 31 that are divided into two in the circumferential direction, and is assembled to the bearing assembling recesses 7 and 9 of both divided housing bodies 6 and 8, respectively.
Both the outer ring divided bodies 21 and 31 are configured by the same parts having the same shape. And the semicircular division | segmentation track surfaces 22 and 32 are formed in the internal peripheral surface of both the outer ring | wheel division bodies 21 and 31, respectively.

Due to an assembly error due to the fastening of the bolts 4 of the split housing bodies 6 and 8, a slight misalignment occurs on the split surfaces 23 and 33 of the outer ring split bodies 21 and 31 together with the split housing bodies 6 and 8. Therefore, the split raceway surfaces 22 and 32 of the outer ring split bodies 21 and 31 are matched with the split surfaces 23 and 33 of the outer ring split bodies 21 and 31 to form a curved or arcuate first shape. The flank faces 25 and 35 are respectively formed.
In the first embodiment, as shown in FIG. 2, the first flank 25 (35) of the outer ring divided body 21 (31) is separated from the divided surface 23 (33) of the outer ring divided body 21 (31) and the center of the bearing raceway. It has a center O2 on the line L1 connecting O1 and is formed in an arc shape with a radius of curvature R1 smaller than that of the divided track surface 22 (32).

As shown in FIG. 2, between the first flank surfaces 25, 35 of the outer ring divided bodies 21, 31 and the divided raceway surfaces 22, 32, the side connected to the first flank surfaces 25, 35 is deeply divided. Second flank surfaces 26 and 36 each having a curved surface or a circular arc surface that become shallower as approaching the surfaces 25 and 35 are formed.
In the first embodiment, as shown in FIG. 2, the second flank 26 (36) of the outer ring divided body 21 (31) includes the second flank 26 (36) and the first flank 25 (35). ) On the line L2 connecting the joint point P1 and the bearing track center O1 with a radius of curvature R2 having a center O3.

  Moreover, in this Example 1, as shown in FIG. 3, the division | segmentation track surface 22 (at the intersection P2 of the division | segmentation track surface 22 (32) of the outer ring split body 21 (31) and the 1st flank 25 (35) is shown. 32) and the first flank L4 formed by the tangent L3 of the first flank 25 (35), and θ, the intersection P3 of the divided raceway surface 22 (32) and the second flank 26 (36). When the second clearance angle formed by the tangent line L5 of the split track surface 22 (32) and the tangent line L6 of the second clearance surface 26 (36) is β, the relationship is set so that “θ> β”. It is desirable that

  Further, as shown in FIG. 4, the depth (maximum depth) of the first flank 25 (35) is a, and the depth (maximum depth) of the second flank 26 (36) is b. When the displacement amount (assumed maximum displacement amount) of the split surfaces 23 and 33 of both outer ring divided bodies 21 and 31 is δ and the elastic deformation amount of the rolling element 15 is δγ, “a> δ”, “ It is desirable to set so as to satisfy the relationship “b> δγ”.

The split rolling bearing according to the first embodiment is configured as described above.
Therefore, as shown in FIG. 5, due to an assembly error due to bolting of both the split housing bodies 6, 8 of the housing 5, the split surfaces 23 of the outer ring split bodies 21, 31 together with these split housing bodies 6, 8, A slight displacement at 33 may occur.
When the rolling element 15 passes through the step due to the positional displacement of the split surfaces 23 and 33 of the outer ring split bodies 21 and 31 during rotation of the bearing in a state where the split surfaces 23 and 33 of the outer ring split bodies 21 and 31 are misaligned. The problem of the rolling element 15 colliding with the edge portion of the step can be suppressed by the first flank 25 of the one outer ring divided body 21.
In particular, the rolling element 15 that has passed through the first flank 25 is subsequently guided by the second flank 26 and rolls toward the divided track surface 22. For this reason, it is possible to satisfactorily suppress vibration, noise, damage, and the like caused by the steps generated between the split surfaces 23 and 33 of the outer ring split bodies 21 and 31.
As a result, it is possible to provide a split type rolling bearing excellent in quietness and durability.

Moreover, in this Example 1, as shown in FIG. 2, the 1st flank 25 (35) of the outer ring division body 21 (31) is the bearing surface 23 (33) of the outer ring division body 21 (31), and a bearing. It has a center O2 on a line L1 connecting the track center O1 and is formed in an arc shape with a smaller radius of curvature than the divided track surface 22 (32).
Further, the second flank 26 (36) of the outer ring divided body 21 (31) is connected to the junction point P1 between the second flank 26 (36) and the first flank 25 (35) and the bearing track center O1. Are formed in an arc shape with a radius of curvature having a center O3 on a line L2 connecting the two.
As a result, the first and second flank surfaces 25 and 26 (35 and 36) of the outer ring divided body 21 (31) can be easily and accurately polished with the rotary polishing grindstone.

In addition, as shown in FIG. 3, when the first clearance angle θ and the second clearance angle β are set so as to satisfy the relationship “θ> β”, the rolling element 15 smoothly rolls. Therefore, it is effective for suppressing vibration, abnormal noise, damage and the like.
Further, as shown in FIG. 4, the depth (maximum depth) of the first flank 25 (35) is a, and the depth (maximum depth) of the second flank 26 (36) is b. When the displacement amount (assumed maximum displacement amount) of the split surfaces 23 and 33 of both outer ring divided bodies 21 and 31 is δ and the elastic deformation amount of the rolling element 15 is δγ, “a> δ”, “ When the relationship is set so as to satisfy “b> δγ”, the rolling of the rolling element 15 is further smoothed, and thus the effect of improving quietness and durability is great.

In addition, this invention is not limited to the said Example 1, In the range which does not deviate from the summary of this invention, it can also be implemented with a various form.
For example, in the first embodiment, the case where the split type rolling bearing 10 rotatably supports the crankshaft 1 of the internal combustion engine on both the split housing bodies 6 and 8 of the housing 5 is illustrated. Even in the case of rotatably supporting the two split housing bodies, the split rolling bearing of the present invention can be employed.

DESCRIPTION OF SYMBOLS 1 Crankshaft 5 Housing 6, 8 Split housing body 10 Split type rolling bearing 15 Rolling body 20 Outer ring member 21, 31 Outer ring split body 22, 32 Split raceway surface 23, 33 Split surface 25, 35 First flank 26, 36 Second flank

Claims (2)

A split-type rolling bearing composed of both outer ring divided bodies in which the outer ring member is divided into two in the circumferential direction,
The split raceway surfaces of the outer ring divided bodies are formed with first flank surfaces that are matched with the split surfaces of the outer ring split bodies to form a curved or arcuate shape,
Between the first flank and the divided raceway surface, a second flank that forms a curved surface or an arc surface that is deeper on the side connected to the first flank surface and becomes shallower as it approaches the divided raceway surface. Formed ,
The first flank has a center on a line connecting the split surface of the outer ring split body and the bearing raceway center and is formed in an arc shape with a smaller radius of curvature than the split raceway surface,
The second flank is formed in an arc shape with a radius of curvature having a center on a line connecting a junction between the second flank and the first flank and the bearing raceway center. Split-type rolling bearing. The split rolling bearing according to claim 1 ,
A first flank angle formed by the tangent line of the split raceway surface and the tangent line of the first flank surface from the intersection of the split raceway surface and the first flank surface is defined as θ, and the split raceway surface and the second flank surface are When the second relief angle formed by the tangent line of the split raceway surface and the tangent line of the second flank from the intersection of
A split type rolling bearing characterized by being set to have a relation of “θ> β”.

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