CN115962226A

CN115962226A - Cylindrical roller bearing

Info

Publication number: CN115962226A
Application number: CN202211178386.6A
Authority: CN
Inventors: 阴山和气
Original assignee: NTN Corp
Current assignee: NTN Corp
Priority date: 2021-10-12
Filing date: 2022-09-26
Publication date: 2023-04-14
Also published as: WO2023063043A1; JP2023057850A; CN218440256U

Abstract

The present invention provides a cylindrical roller bearing which can restrict the maximum movement of cylindrical rollers, has excellent vibration resistance, realizes improvement of durability, and can effectively prevent reduction of service life. And avoidance parts are arranged at four corners of the groove. The roller diameter of the cylindrical roller is set to Dw, and the radial movable amount/Dw of the groove center with respect to the roller center is 3% to 10%.

Description

Cylindrical roller bearing

Technical Field

The present invention relates to a cylindrical roller bearing.

Background

The cage used for the bearing has a function of holding the rolling elements at equal intervals in the bearing to prevent the rolling elements from contacting each other, and contributing to high-speed rotation. The holder includes a punched holder (press holder), a cut holder (cutting holder), a molded holder by injection molding or the like, and the like.

As a cut holder, a cut holder described in patent document 1 is known. As shown in fig. 10, the cut retainer is composed of two concentric ring portions 1 and a column portion 2 connecting the ring portions. Cylindrical rollers 4 as rolling elements are accommodated in pockets 3 formed between the adjacent column parts 2. Furthermore, relief portions 5 are formed at each corner of the recessed groove 3.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 11-218135

Disclosure of Invention

Problems to be solved by the invention

However, the relief portion in the cut retainer is formed by turning such as drilling. However, if such machining is performed, the side surface of the arc-shaped pillar portion is cut into the groove, and the strength of the pillar portion is reduced. That is, in the one-piece cut retainer, since the relief portion 5 is formed by drilling, it takes the form of a straight hole parallel to the center line of the recessed groove toward the center of the retainer. Therefore, the relief portion 5 needs to go over the side surface of the arc-shaped pillar portion 2 and cut into the pillar portion 2 side. In this case, the strength of the pillar portion 2 is determined by the cross section passing through the bottom of the pillar portion 2, which is the narrowest portion, and therefore the cross sectional area is small and the strength is poor. In addition, as the cage, it is preferable to provide a cage having excellent vibration resistance for the purpose of prolonging the life of the bearing, improving the durability, and the like.

In view of the above circumstances, the present invention provides a cylindrical roller bearing using a cut cage excellent in strength and durability without reducing the bearing life.

Means for solving the problems

The cylindrical roller bearing of the present invention comprises: a pair of raceway rings; a plurality of cylindrical rollers as rolling elements interposed between raceway surfaces of the pair of raceway rings; and a one-piece type cut holder, wherein,

the integrated cut holder includes: a pair of annular portions; a plurality of column portions extending in the axial direction and connecting the pair of annular portions; and a recessed groove formed between the adjacent column portions and accommodating the cylindrical rollers, wherein the integrated cut retainer includes relief portions at four corners of the recessed groove and holds the cylindrical rollers at predetermined intervals in a circumferential direction, and wherein when a roller diameter of the cylindrical rollers is set to Dw and a ratio of a radial movable amount of a center of the recessed groove with respect to a roller center to the roller diameter is set to Φ 1, Φ 1= (radial movable amount/Dw of the center of the recessed groove with respect to the roller center) is 3% to 10%.

The maximum movement of the cage can be restricted by evaluating the clearance generated between the roller diameter and the pocket diameter with respect to the amount of radial movement of the pocket center with respect to the roller center. In the cut cage of the present invention, the pocket opening portion on the cage outer diameter side is smaller than the pocket opening portion on the cage inner diameter side, and since any opening portion is smaller than the roller diameter, the roller is sandwiched from the cage inner diameter side. The roller center was aligned with the groove center, the value of the radial distance when the cage outer diameter side was moved into contact with the roller and the value of the radial distance when the cage inner diameter side was moved into contact with the roller were compared, and the larger value was evaluated as the amount of radial movement of the groove center with respect to the roller center. The same evaluation method was also applied to the cage having the smaller pocket opening portion on the inner diameter side than the outer diameter side.

Preferably, the side surface of the pillar portion from which the escape portion is omitted is a linear portion extending in the axial direction, and when the axial length of the linear portion is H2 and the roller length is H1, and the ratio of the axial length to the roller length is Φ 2, Φ 2= (H2/H1) is 60% to 90%.

By setting in this way, a flow path of the lubricating oil can be sufficiently ensured, and the lubricating oil is excellent in vibration resistance and is less likely to wear.

Preferably, when a torus-crowned circle diameter of a roller-end-surface-corresponding surface of the groove which is an inner wall surface of the torus is Dx and a roller diameter is Dw, and a ratio of the torus-crowned circle diameter to the roller diameter is Φ 3, Φ 3= (Dx/Dw) is 55% to 75%.

Even in the case of such setting, a flow path of the lubricating oil can be sufficiently ensured, and the vibration resistance is excellent and the wear is not easily caused.

Preferably, in a cross section perpendicular to an axis of the retainer, a side surface of the pillar portion is arc-shaped, the relief portion is parallel to the side surface of the pillar portion, and a shape of the relief portion includes: a first parallel portion parallel to a side surface of the pillar portion connected to the side surface of the pillar portion via a first slope portion; a second parallel portion parallel to an inner wall surface of the annular portion connected via a second inclined surface portion and the inner wall surface of the annular portion; and a curved surface portion that is in contact with the first parallel portion and the second parallel portion, connects the first parallel portion and the second parallel portion, and does not interfere with a chamfered portion of the cylindrical roller, and when an inclination angle between the first inclined surface portion and a side surface of the pillar portion is θ 1 and an inclination angle between the second inclined surface portion and an inner wall surface of the annular portion is θ 2, θ 1 > θ 2, 30 ° < θ 1 < 45 °,2 ° < θ 2 < 15 °.

By setting as above, θ 1 can be made relatively large, and the cross-sectional area of the space of the relief portion in the circumferential direction can be increased, which is advantageous for supplying the lubricant. Further, since the cylindrical roller rotates in the circumferential direction, the larger escape portion in the column portion direction is advantageous for lubrication, and the escape portion is a curve parallel to the column portion, which is advantageous for lubrication. Further, θ 2 can be made smaller than θ 1, and the spatial cross-sectional area can also be made smaller. Since the annular portion with which the roller end surface contacts is narrower than the column portion, the strength is reduced when the relief portion is provided to be large.

Effects of the invention

The present invention can restrict the maximum movement of the cylindrical roller, and therefore, the present invention is excellent in vibration resistance, can improve durability, and can effectively prevent a reduction in life.

Drawings

Fig. 1 is a sectional view of a cylindrical roller bearing of the present invention.

Fig. 2 is a main portion perspective view of a cut retainer for a cylindrical roller bearing.

Fig. 3 is a sectional view showing a pillar portion of the cut retainer.

Fig. 4 is a sectional view showing a roller end surface corresponding surface of the cut cage.

Fig. 5 is a main part development view of the cut holder.

Fig. 6 is an enlarged view of a main portion of fig. 5.

Fig. 7 is a schematic cross-sectional view showing the relationship between the groove and the roller.

Fig. 8 is a schematic cross-sectional view showing the relationship between the side surface of the pillar portion and the roller.

Fig. 9 is a schematic view showing a relationship between the roller and the inner wall surface of the annular portion.

Fig. 10 is a sectional view of a cut cage used in a conventional cylindrical roller bearing.

Description of the reference numerals:

11. rolling way ring (inner ring)

11a raceway surface

12. Raceway ring (outer ring)

12a raceway surface

20. Cylindrical roller

20a end face

21. Annular part

21a inner wall surface

23. Post part

23a side surface

24. Groove

25. Avoiding part

31. First inclined plane part

32. Second inclined plane part

33. Curved surface part

34. A first parallel part

35. Second parallel part

Center of O1 roller

O2 groove center.

Detailed Description

Hereinafter, embodiments of the present invention will be described with reference to fig. 1 to 9. Fig. 1 is a cross-sectional view of a cylindrical roller bearing according to the present invention, which includes a pair of raceway rings, a plurality of rolling elements interposed between raceway surfaces of the pair of raceway rings, and a cage that holds the rolling elements at predetermined intervals in a circumferential direction.

In this case, the cage includes an inner ring 11 constituting one raceway ring, an outer ring 12 constituting the other raceway ring, cylindrical rollers 20 as rolling elements interposed between a raceway surface 11a of the inner ring 11 and a raceway surface 12a of the outer ring 12, and a cage 14 held at a predetermined interval in a circumferential direction. In the bearing shown in this figure, the outer ring has

flange portions

12b, 12b at both axial ends thereof, and the inner ring 11 has no flange portions at both axial ends thereof, and is formed in a so-called single row NU shape including inner-ring tapered

portions

15b, 15 b.

The inner ring 11 and the outer ring 12 are made of, for example, high-carbon chromium bearing steel such as JIS SUJ2, alloy for machine structure such as SCM420, or carbon steel for machine structure such as S53C. The cylindrical rollers 20 serving as rolling elements may be made of an iron-based metal material, ceramic, or the like. Examples of the iron-based metal material include bearing steel used for a rolling bearing or the like, carburized steel, carbon steel for machine structural use, cold rolled steel, hot rolled steel, and the like. In addition, carbon steel for machine structural use and high-strength brass casting are often used as the material of the retainer 14, and aluminum alloy and the like are also used.

However, as shown in fig. 2 to 5, the retainer 14 includes: a pair of

annular portions

21, 21; a plurality of column portions 23 extending in the axial direction and connecting the pair of

annular portions

21, 21; and a groove 24 formed between the

adjacent pillar portions

23, 23 and accommodating the cylindrical roller 20. In addition, relief portions 25 are formed at four corners of the concave groove 24.

The side surface of the column portion 23 is arc-shaped in a cross section perpendicular to the axis of the holder, and the relief portion 25 extends parallel to the side surface of the column portion 23. In general, when simply called parallel, it refers to a relationship between a straight line and a straight line, between a plane and a plane, or between a straight line and a plane, but as a mathematical expression such as parallel curves (parallel curves) exists, a term such as parallel may be used for curves. A parallel curve is defined as two curves having a common normal at any point. To which (part of) concentric circles belong. The term "parallel" in the present description and claims is also used in this sense. That is, since the escape portion is parallel to the arc-shaped pillar portion side surface, the escape portion is also arc-shaped. In other words, in a cross section perpendicular to the axis of the retainer, the side surface of the column portion 23 and the relief portion 25 are in an arc shape having a common center and different radii of curvature, and are in a relationship of constituting a part of a concentric circle.

Fig. 6 shows the bypass portion 25 in detail. The profile of the escape portion 25 includes: a first inclined surface portion 31 formed of an inclined surface forming an acute angle with the side surface 23a of the pillar portion 23; a second inclined surface portion 32 formed of an inclined surface forming an acute angle with an inner wall surface (side surface) of the annular portion (side plate) 21; a first parallel portion 34 offset from the side surface 23a of the pillar portion 23 in the circumferential direction to the opposite-to-recessed groove side by a1; and a second parallel portion 35 offset from the inner wall surface 21a of the annular portion (side plate) 21 in the axial direction by a2 toward the opposite side of the groove. Further, the first parallel portion 34 and the second parallel portion 35 are connected by the curved surface portion 33. Therefore, the first inclined surface portion 31, the first parallel portion 34, the curved surface portion 33, the second parallel portion 35, and the second inclined surface portion 32 of the escape portion 25 are continuously continuous from the side surface 23a of the pillar portion 23 to the inner wall surface 21a of the annular portion (side plate) 21. By having an angle at which the forming cutter (bite) for forming the relief portion 25 is positioned, the relief portion 25 can be reliably formed at a position outside the side surface 21a (the side opposite to the recess) and outside the side surface 23a of the column portion 23 (the side opposite to the recess). The first parallel portion 34 and the second parallel portion 35 form a tangent line with respect to the curved surface portion 33. In fig. 6, R represents a radius of curvature of the curved surface portion 33, and R represents a radius of curvature of the rounded portion 24c of the concave groove 24 when the relief portion 25 is not formed.

The allowable ranges of the dimensions a1, a2, and R (the radius of curvature of the curved surface portion 33) are ranges that do not interfere with the chamfered portion of the cylindrical roller 20.

When the inclination angle of the first inclined plane part is theta 1 and the inclination angle of the second inclined plane part is theta 2, the relation between theta 1 and theta 2 is theta 1 > theta 2. Further, θ 1 is set to 30 ° < θ 1 < 55 °, and θ 2 is set to 2 ° < θ 2 < 15 °.

Fig. 7 shows the relationship between the pockets 24 of the retainer and the cylindrical rollers 20 accommodated in the pockets 24. In the cage of the present invention, when the roller diameter of the cylindrical roller 20 is Dw and the ratio of the radial movable amount of the groove center O2 with respect to the roller center O1 to the roller diameter is Φ 1, Φ 1= (radial movable amount/Dw of the groove center O2 with respect to the roller center O1) is 3% to 10%. The cylindrical roller 20 in fig. 7 is shown in a state of abutting against the outer diameter edges 24b, 24b of the groove 24. Also, the groove center O2 is located on the bearing p.c.d.

Fig. 8 shows the relationship between the side surface of the pillar portion 23 and the cylindrical roller 20. In this case, the side surface 23a of the column part 23 from which the escape part 25 is omitted is a linear part extending in the axial direction, and when the axial length of the linear part is H2 and the roller length is H1, and the ratio of the axial length to the roller length is Φ 2, Φ 2= (H2/H1) is 60% to 90%.

Fig. 9 shows a relationship between the cylindrical roller 20 and the inner wall surface of the annular portion 21. Phi 3= (Dx/Dw) is 55% to 75% where Dx is the torus equator diameter of the face corresponding to the roller end face 20a of the groove 24 as the inner wall face 21a of the toroidal portion 21 and Dw is the roller diameter, and the ratio of the torus equator diameter to the roller diameter is phi 3.

In the present cylindrical roller bearing, the clearance generated between the roller diameter and the pocket diameter is evaluated with respect to the amount of radial displacement of the pocket center O2 with respect to the roller center O1, and the maximum displacement of the cage can be restricted. In the cut cage 14 of the present invention, since the pocket opening portion on the cage outer diameter side is smaller than the pocket opening portion on the cage inner diameter side and any opening portion is smaller than the roller diameter, the roller 20 is sandwiched from the cage inner diameter side. The roller center O1 and the pocket center O2 are aligned, and the value of the radial distance when the outer diameter side of the cage 14 is moved to contact with the roller and the value of the radial distance when the inner diameter side of the cage is moved to contact with the roller 20 are compared, and the larger value is evaluated as the amount of radial movement of the pocket center O2 with respect to the roller center O1. The same evaluation method was also applied to the cage having the smaller pocket opening portion on the inner diameter side than the outer diameter side.

Therefore, the present cylindrical roller bearing can restrict the maximum movement of the cylindrical rollers 20, and therefore, is excellent in vibration resistance, can improve durability, and can effectively prevent a reduction in service life.

In the cut retainer of the embodiment, the relief portion 25 can be parallel to the side surface 23a of the column portion 23, and has the same size in any cross section in the thickness direction of the column portion 23. Therefore, the degree of reduction in the cross-sectional area of the root portion of the pillar portion 23 is minimized. Further, the area of the relief portion 25 recessed in the root portion of the column portion 23 can be reduced, and stress concentration can be relaxed compared to the conventional one.

In particular, by setting Φ 1= (the radial movable amount/Dw of the groove center O2 with respect to the roller center O1) to 3% to 10%, the maximum movement of the cylindrical roller 20 can be restricted with respect to the radial movable amount of the groove center O2 with respect to the roller center O1.

Therefore, in the present cage, the reduction in the cross-sectional area of the root portion of the column portion 23 can be minimized, the decrease in strength due to the provision of the relief portion 25 can be suppressed, the vibration resistance is excellent, the durability can be improved, and the reduction in the life can be effectively prevented.

The side surface 23a of the column part 23 where the relief portion 25 is omitted is a linear part extending in the axial direction, and when the axial length of the linear part is H2 and the ratio of the axial length of the linear part to the roller length is Φ 2 when the roller length is H1, Φ 2= (H2/H1) is preferably 60% to 90%.

By setting in this way, a flow path for the lubricating oil can be sufficiently ensured, and the lubricating oil is excellent in vibration resistance and less likely to wear.

When the torus equator diameter of the surface corresponding to the roller end surface 20a of the concave groove 24 which is the

inner wall surfaces

21a, 21a of the

annular portions

21, 21 is Dx and the ratio of the torus equator diameter to the roller diameter when the roller diameter is Dw is Φ 3, Φ 3= (Dx/Dw) is preferably 55% to 75%.

Even in the case of such setting, a flow path of the lubricating oil can be sufficiently ensured, and the lubricating oil is excellent in vibration resistance and is less likely to wear.

When the inclination angle between the first inclined surface portion 31 and the side surface 23a of the pillar portion 23 is θ 1 and the inclination angle between the second inclined surface portion 32 and the inner wall surfaces 21a and 21a of the annular portion 21 is θ 2, θ 1 > θ 2, 30 ° < θ 1 < 45 °, and 2 ° < θ 2 < 15 ° are preferable.

Thus, by making θ 1 larger than θ 2, dimension a1 is larger than dimension a2. Since the cylindrical roller 20 rotates in the circumferential direction except that the relief portion 25 is a curved line parallel to the pillar portion 23, the relief portion 25 in the pillar portion direction is larger than the relief portion 25 in the annular portion direction, which is advantageous for lubrication. Further, since θ 2 is smaller than θ 1 and the dimension a2 is smaller than the dimension a1, the relief portion 25 in the annular portion direction is smaller than the relief portion 25 in the column portion direction, and a decrease in strength of the

annular portions

21 and 21 thinner than the column portion 23 can be suppressed.

The retainer having the relief portion 25 shown in fig. 6 is evaluated by using evaluation functions of Φ 1, Φ 2, and Φ 2. The evaluation using the evaluation function of φ 1 is shown in Table 1 below.

[ Table 1]

φ1[％]	2	3	…	10	15
							×	○	…	○	×

If Φ 1 is 15% or more, the space in the pocket becomes excessively wide, the amount of movement between the roller 20 and the cage 14 in the pocket 24 becomes large, and the amount of vibration becomes large. However, when the cylindrical rollers 20 are assembled to the bearing, the cylindrical rollers 20 are first inserted into the pockets 24 of the cage 14 from the inner diameter side, and then assembled to the inner ring 11. Therefore, if the space in the pocket becomes excessively wide, the cylindrical roller 20 may fall from the retainer inner diameter side. On the other hand, if Φ 1 is 2% or less, the groove space becomes too narrow, and a flow path for a lubricant (oil, grease, or the like) cannot be secured, and the cylindrical rollers 20 may be locked, which may prevent smooth rotation as a bearing. Further, the assembling property of the cylindrical rollers 20 to the cage 14 is poor. In table 1, "o" indicates that the groove inner space is not too narrow or too wide and does not cause the above-described problem, and "x" indicates that the groove inner space is too wide (15% or more) and may cause the above-described problem, and that the groove inner space is too narrow (2% or less) and may cause the above-described problem. Therefore, in this case, o indicates superiority, and x indicates no superiority.

Therefore, in the present retainer, Φ 1 is set to 3% to 10%. Thus, the retainer can sufficiently secure a flow path for the lubricating oil, and is excellent in vibration resistance and less likely to wear.

Next, the evaluation using the evaluation function of Φ 2 is shown in table 2 below.

[ Table 2]

φ2[％]	55	60	…	90	95
							×	○	…	○	×

If Φ 2 is 95% or more, a sufficient flow path for the lubricating oil cannot be secured, and it becomes difficult to stably obtain smooth rotation over a long period of time. When Φ 2 is 55% or less, the contact portion between the cylindrical roller 20 and the pillar portion 23 is reduced, the vibration resistance is poor, and the wear is easy. Further, the strength of the column portion 23 or the entire retainer may be insufficient. In table 2, a value "o" indicates that a sufficient flow path for the lubricating oil can be secured and the contact portion between the cylindrical roller 20 and the pillar portion is not reduced, so that the above-described problem does not occur, and a value "x" indicates that a sufficient flow path for the lubricating oil cannot be secured (Φ 2 is 95% or more) and the above-described problem may occur, and that the contact portion between the cylindrical roller 20 and the pillar portion 23 is reduced (Φ 2 is 55% or less) and the above-described problem may occur. Therefore, in this case, o indicates superiority, and x indicates no superiority.

Therefore, in the present retainer, Φ 2 is set to 60% to 90%. Even in the case of such setting, a flow path of the lubricating oil can be sufficiently ensured, and the vibration resistance is excellent and the wear is not easily caused.

Next, the evaluation of the evaluation function based on Φ 3 is shown in table 3 below.

[ Table 3]

φ3[％]	50	55	…	75	80
							×	○	…	○	×

If Φ 3 is 80% or more, a sufficient flow path for the lubricating oil cannot be secured, and it becomes difficult to stably obtain smooth rotation over a long period of time. If Φ 3 is 50% or less, the contact portion between the roller end face 20a and the annular portion 21 is reduced, the vibration resistance is poor, and the wear is easy. Further, the strength of the annular portion 21 or the holder as a whole may be insufficient. In table 3, o indicates that a sufficient flow path for the lubricating oil can be secured and the contact portion between the cylindrical roller 20 and the annular portion 21 is not reduced, and the problem point is not generated, x indicates that a flow path for the lubricating oil cannot be secured sufficiently (Φ 3 is 80% or more) and the problem may be generated, and that the contact portion between the cylindrical roller 20 and the annular portion 21 is reduced (Φ 3 is 50% or less) and the problem may be generated. Therefore, in this case, o indicates superiority, and x indicates no superiority.

Therefore, in the present retainer, Φ 3 is set to 55% to 75%. Even in the case of such setting, a flow path of the lubricating oil can be sufficiently ensured, and the lubricating oil is excellent in vibration resistance and is less likely to wear.

The cylindrical roller bearing of the present invention uses the above-described retainer 14. Therefore, the cylindrical roller bearing can constitute a bearing as follows: the vibration-resistant steel sheet is excellent in vibration resistance while suppressing a decrease in strength, and can improve durability and effectively prevent a decrease in life.

The embodiments of the present invention have been described above, but the present invention is not limited to the embodiments described above, and various modifications are possible, and the bearing is NU-shaped in the embodiments, but may be NJ-shaped, NUP-shaped, N-shaped, NF-shaped, NH-shaped, and the like. Here, NJ-shape means a shape having a flange on one side of the inner ring and flanges on both sides of the outer ring, NUP-shape means a shape having a flange on one side of the inner ring, flanges on both sides of the outer ring, and a flanged ring combined on the inner ring side, N-shape means a shape having flanges on both sides of the inner ring and no flange on the outer ring, NF-shape means a shape having flanges on both sides of the inner ring and flanges on one side of the outer ring, and NH-shape means a shape having an L-shaped flanged ring combined on the inner ring side of NU-shape or NJ-shape.

In the cylindrical roller bearing shown in fig. 1, since the cylindrical roller bearing is disposed on the outer diameter side of the roller pitch circle, an outer ring guide system can be adopted as the roller bearing. Here, the outer ring guide is a guide surface in which the retainer is positioned by abutting the retainer against the outer ring, and the outer surface of the guide surface abuts against the inner periphery of the outer ring. Similarly, in the case of a cylindrical roller bearing having flange portions on both sides of the inner ring, an inner ring guide system can be adopted. Here, the inner ring guide is a guide surface that positions the cage by bringing the cage into contact with the inner ring, and the inner diameter surface comes into contact with the outer periphery of the inner ring.

Industrial applicability

The cylindrical roller bearing can be used for applications involving vibrations such as a speed-up gear, and can be used for various devices, structures, and the like such as general machines, electric machines, and transport machines. The bearing is not limited to a single row type, and may be a multiple row type.

Claims

1. A cylindrical roller bearing is provided with: a pair of raceway rings; a plurality of cylindrical rollers serving as rolling elements interposed between raceway surfaces of the pair of raceway rings; and an integral type cut holder, and a method of manufacturing the same,

the integrated cut holder includes: a pair of annular portions; a plurality of column portions extending in the axial direction and connecting the pair of annular portions; and pockets formed between the adjacent column parts and accommodating the cylindrical rollers, the one-piece cut cage being provided with relief portions at four corners of the pockets and holding the cylindrical rollers at predetermined intervals in a circumferential direction,

it is characterized in that the preparation method is characterized in that,

when the roller diameter of the cylindrical roller is set to Dw and the ratio of the radial movable amount of the groove center with respect to the roller center to the roller diameter is set to Φ 1, ± 1= the radial movable amount/Dw of the groove center with respect to the roller center, and Φ 1 is 3% to 10%.

2. Cylindrical roller bearing according to claim 1,

the side surface of the pillar portion where the escape portion is omitted is a straight portion extending in the axial direction, and when the axial length of the straight portion is H2 and the ratio of the axial length to the roller length when the roller length is H1 is Φ 2, Φ 2= H2/H1, and Φ 2 is 60% to 90%.

3. Cylindrical roller bearing according to claim 1 or 2,

phi 3= Dx/Dw, and phi 3 is 55% to 75% where Dx is the torus equator diameter of the roller end face corresponding face of the groove as the inner wall face of the torus, and phi 3 is the ratio of the torus equator diameter to the roller diameter when Dw is the roller diameter.

4. Cylindrical roller bearing according to any one of claims 1 to 3,

in a cross section perpendicular to an axis of the retainer, a side surface of the pillar portion is arc-shaped, the escape portion is parallel to the side surface of the pillar portion, and a shape of the escape portion includes: a first parallel portion parallel to a side surface of the pillar portion connected to the side surface of the pillar portion via a first slope portion; a second parallel portion parallel to an inner wall surface of the annular portion connected via a second inclined surface portion and the inner wall surface of the annular portion; and a curved surface portion that is in contact with the first parallel portion and the second parallel portion, connects the first parallel portion and the second parallel portion, and does not interfere with a chamfered portion of the cylindrical roller, and when an inclination angle between the first inclined surface portion and a side surface of the pillar portion is θ 1 and an inclination angle between the second inclined surface portion and an inner wall surface of the annular portion is θ 2, θ 1 > θ 2, 30 ° < θ 1 < 45 °,2 ° < θ 2 < 15 °.