WO2017110905A1

WO2017110905A1 - Roller bearing

Info

Publication number: WO2017110905A1
Application number: PCT/JP2016/088171
Authority: WO
Inventors: 貴行鈴木; 清茂山内
Original assignee: Ntn株式会社
Priority date: 2015-12-24
Filing date: 2016-12-21
Publication date: 2017-06-29
Also published as: JP2017115977A

Abstract

In the present invention, wear and seizing of the guiding portion of a holder and abnormal wear of a columnar part of the holder are prevented even when a planetary rotational element provided to a planetary reduction gear is supported by roller bearings. Holder guiding surfaces (9, 10) are provided to the inner periphery of an outer race (2). The present invention is provided with a first ring (12) anchored to a first annular part (14) of a holder body (11), and a second ring (13) anchored to a second annular part (15) of the holder body (11). The first ring (12) and the second ring (13) are provided with guided surfaces (18, 19) that have a lower coefficient of friction than the surface of the holder body (11). The first ring (12) and the second ring (13) are formed into annular configurations from a material having a higher modulus of elasticity than the material of the holder body (11).

Description

Roller bearing

The present invention relates to a roller bearing suitable for a revolving part such as a planetary rotating body provided in a planetary speed reducer, and particularly to guiding a cage.

In dump trucks and the like, planetary speed reducers that provide a large reduction ratio are arranged inside the wheel rim. The planetary rotating body provided in the planetary reduction gear is composed of a planetary gear or a planetary roller that revolves while rotating between a ring gear and a sun gear, and is supported by a carrier pin via a rolling bearing. As the rolling bearing, a roller bearing such as a tapered roller bearing or a cylindrical roller bearing is employed (for example,

Patent Documents

1 and 2 below).

Generally, roller bearings are provided with a cage for maintaining a circumferential interval between the rollers. In the cage, pockets for storing rolling elements are formed at equal intervals in the circumferential direction. In the case of roller bearings used for revolving parts such as for supporting planetary rotors, in addition to centrifugal force due to rotation around the bearing center axis of the cage, rolling bearings are included in the cage and the lubricating oil inside the bearing. Centrifugal force by revolving together with the planetary rotating body also acts. The centrifugal force due to the revolving motion causes a load region in the rolling bearing and causes deformation and eccentricity of the cage and bias of the lubricating oil inside the bearing. When the rolling element guide method as in Patent Document 1 is adopted as the cage guide method, some column parts are strongly brought into contact with the rollers due to the eccentricity of the cage in the load region where the lubrication condition is bad, and the column parts are abnormal. There is a risk of wear or breakage due to a bending moment where the column portion is concentrated at the root portion connected to the annular portion. In order to avoid this, it is preferable to employ a raceway guide type cage (for example,

Patent Documents

3 and 4 below).

The roller bearing disclosed in Patent Document 3 forms a guided surface composed of a plate-thick surface at the tip of a protruding piece that is partially cut and raised from a small-diameter side annular portion of a steel plate cage, and the outer ring of the inner ring or the outer ring A cage guide surface is formed on the inner periphery, and the cage can be guided by contact between the guided surface and the cage guide surface.

In the roller bearing disclosed in Patent Document 4, a cage guide surface is formed on the outer periphery of the outer ring, and a guided surface that faces the cage guide surface in the radial direction is formed on an extended portion of the annular portion of the cage. The cage can be guided by contact between the guided surface and the cage guide surface.

When the cage is guided by the outer ring rotating together with the planetary rotator as in Patent Document 4, the relative speed between the cage guide surface of the outer ring and the guided surface of the cage is compared with the case of the inner ring guide. Since the difference is reduced and the circumference of the cage guide surface and the guided surface is increased to increase the contact area during guidance, wear and seizure of the cage guide surface and the guided surface can be prevented.

JP 2012-202417 A JP 2013-72504 A JP 2004-293730 A JP 2008-196582 A

However, since the roller bearing disclosed in Patent Document 4 guides the cage on the outer circumference of the outer ring, at least one of the annular portions of the cage is opposed to the cage guide surface on the outer circumference of the outer ring in the radial direction. There is a concern that the total width of the bearing may be increased. Further, since the cage extension part passes on the outer diameter side of the outer ring through the outer diameter side of the outer ring, the side surface of the outer ring on the inner diameter small diameter side cannot be fixed by abutting against other members such as the housing shoulder. . For this reason, the combination of the pair of roller bearings is limited to the front combination, and a preload cannot be applied to the roller bearings. If preload is not applied to the roller bearing, the support of the planetary rotating body may not be stable due to the internal clearance of the positive bearing, which may interfere with the normal operation of the planetary rotating body, for example, the normal meshing of the planetary gear. .

On the other hand, as in the case of the roller bearing of Patent Document 3, the cage is guided by contact between the guided surface formed of the plate thickness surface of the projecting piece obtained by cutting and raising the small-diameter side annular portion of the cage and the inner periphery of the outer ring. Although there is no problem such as an increase in the total width of the bearing as in the above-mentioned Patent Document 3, the cage is inclined when the centrifugal force is large, and the contact area between the guided surface and the inner circumference of the outer ring is a line. There is a possibility that it will become small like contact, or it may interfere with the pillar part. When the contact area is narrowed, there is a concern that the contact surface pressure increases or the oil film is cut and wear or seizure occurs. When the roller irregularly interferes with the column part, the column part may be abnormally worn.

In view of the above background, the problem to be solved by the present invention is that even when the planetary rotating body provided in the planetary reduction gear is supported by the roller bearing, the cage guide portion is worn and seized, and the cage column is abnormal. It is to prevent wear.

According to a first aspect of the present invention, there is provided a roller bearing including an inner ring, an outer ring, a plurality of rollers interposed between the inner ring and the outer ring, and a cage that holds the rollers. The cage has an integrally formed cage body, and a first ring and a second ring fixed to the cage body, and the cage body has a first annular portion and a second annular portion. And a pillar portion that divides the two annular portions into pockets, the first ring is fixed to the first annular portion, and the second ring is fixed to the second annular portion. A cage guide surface for guiding the cage in the radial direction is provided only on an inner periphery of the outer ring, and the guided surface guided by the cage guide surface is the cage. Provided on the first ring and the second ring; Inner surface has a low coefficient of friction than the surface of said retainer body is obtained by adopting the configuration that.

According to the first aspect of the present invention, the cage guide surface is provided on the outer ring and the guided surface is provided on the cage, so the cage is guided by the outer ring. In the case of supporting the planetary rotating body provided in the planetary reduction gear, when the cage is guided by the outer ring which is a rotating wheel, the cage between the outer ring and the guided surface of the cage is compared with the inner ring guide. The relative speed difference between the cage surface and the cage guide surface and guided surface becomes longer and the contact surface pressure decreases (so-called PV value suppression), so that the guided surface and cage guide surface wear. And seizure is prevented.
In addition, since the cage guide surface is provided on the inner circumference of the outer ring, the lubricating oil moves to the inner circumference side of the outer ring by the action of a large centrifugal force accompanying the revolution movement of the planetary rotating body. The lubricity of the guided surface is improved. This is also effective in preventing wear and seizure of the guided surface and the cage guide surface in the support application of the planetary rotor.
Furthermore, since the guided surface can be provided with an arbitrary material on the first ring and the second ring which are separate parts from the cage body, the guided surface has a lower coefficient of friction than the surface of the cage body. be able to. Due to the improved slidability on the guided surface, wear and seizure of the cage guide surface and the guided surface are further prevented.
In addition, prevention of wear on the cage guide surface and the guided surface is also effective in preventing abnormal wear of the column portion. That is, as wear of the cage guide surface and guided surface progresses, the clearance (guide clearance) between both surfaces increases. As this enlargement progresses, it eventually becomes a rolling element guide in which the cage is guided by the contact between the roller and the column portion, leading to abnormal wear of the column portion. Therefore, if wear of the cage guide surface and the guided surface is prevented, abnormal wear of the column portion can be prevented.
In addition, since the guided surface and the cage guiding surface can be contacted on both sides in the axial direction of the cage with the pocket as a boundary, a large centrifugal force due to the revolving motion of the planetary rotating body acted on the cage. Even in this case, the tilt of the cage can be suppressed. As a result, a decrease in the contact area between the guided surface and the cage guide surface is suppressed, and abnormal contact with the column portion is also prevented, so that the guided surface and the cage guide surface are more worn and seized. In addition to being prevented, abnormal wear of the column portion is further prevented.

According to a second aspect of the present invention, there is provided a roller bearing including an inner ring, an outer ring, a plurality of rollers interposed between the inner ring and the outer ring, and a cage that holds the rollers. The cage has an integrally formed cage body, and a first ring and a second ring fixed to the cage body, and the cage body has a first annular portion and a second annular portion. And a pillar portion that divides the two annular portions into pockets, the first ring is fixed to the first annular portion, and the second ring is fixed to the second annular portion. A cage guide surface for guiding the cage in the radial direction is provided only on an inner periphery of the outer ring, and the guided surface guided by the cage guide surface is the cage. Provided on the first ring and the second ring; Ring and the second ring, is obtained by adopting the configuration that is formed in an annular shape of a material having a high modulus of elasticity than the material of each said retainer body.

According to the configuration of the second invention, the cage guide surface is provided on the inner circumference of the outer ring, and the guided surface is provided on the outer circumference of the cage, so that the PV value is the same as in the first invention. Suppression and lubricity are improved, and wear of the cage guide surface and the guided surface is prevented.
Furthermore, since the first ring and the second ring, which are separate parts from the cage body, can be made of any material, the first ring and the second ring have a higher elastic modulus than the material of the cage body, respectively. It can be formed in an annular shape by a material having As a result, compared to the case where the cage is made of a single material, the first ring and the second ring improve the rigidity against deformation of the cage. Thereby, abnormal wear of the column part is prevented. That is, a large centrifugal force due to the revolving motion of the planetary rotating body acts on the cage, and the cage is pressed against the cage guide surface of the outer ring and deforms into an ellipse.As a result, the pocket clearance is reduced and the roller and cage are When the column part comes into abnormal contact with the column part, abnormal wear of the column part is caused. Therefore, as the rigidity against the deformation of the cage is improved, the elliptical deformation is suppressed, so that abnormal wear of the column portion is prevented.
In addition, since the guided surface and the cage guide surface can be contacted on both sides in the axial direction of the cage with the pocket as a boundary, the tilt of the cage can be suppressed well as in the first invention. Further, wear and seizure of the guided surface and the cage guide surface are further prevented, and abnormal wear of the column portion is further prevented.

As described above, the roller bearing according to the first invention suppresses the PV value between the guided surface of the cage and the cage guide surface of the outer ring even when the planetary rotating body provided in the planetary reduction gear is supported. The lubricity of the guided surface of the cage and the cage guiding surface of the outer ring is improved, the slidability is improved on the guided surface of the cage, and the cage guiding surface and the guided surface are in contact with each other. Since it is possible to suppress the inclination of the cage, it is possible to prevent wear and seizure of the cage guide surface and the guided surface, which are cage guide portions, and to prevent abnormal wear of the cage pillars.

In addition, the roller bearing according to the second aspect of the present invention suppresses the PV value between the guided surface of the cage and the cage guide surface of the outer ring, even when supporting the planetary rotating body provided in the planetary reduction gear. This improves the lubricity of the guided surface of the cage and the cage guiding surface of the outer ring, and further suppresses elliptical deformation and inclination of the cage when contacting the cage guiding surface and the guided surface. It is possible to prevent wear and seizure of the cage guide surface and the guided surface, which are the cage guide portions, and to prevent abnormal wear of the cage pillars.

Sectional drawing which shows the structure of the roller bearing which concerns on 1st embodiment of this invention. Sectional drawing which shows the structure of a planetary reduction gear provided with the roller bearing which concerns on 1st embodiment. Sectional drawing in the arrow line shown in FIG. Sectional drawing which shows the structure of the roller bearing which concerns on 2nd embodiment of this invention. The side view which shows the structure of the roller bearing which concerns on 3rd embodiment of this invention. Side view of the first ring according to the third embodiment Sectional drawing which shows the structure of the roller bearing which concerns on 4th embodiment of this invention. Sectional drawing which shows the structure of the roller bearing which concerns on 5th embodiment of this invention.

Hereinafter, a roller bearing according to a first embodiment of the present invention will be described with reference to FIG. The roller bearing shown in FIG. 1 includes an inner ring 1, an outer ring 2, a plurality of rollers 3 interposed between the inner ring 1 and the outer ring 2, and a cage 4 that holds these rollers 3. The inner ring 1, the outer ring 2 and the cage 4 are set to the same central axis (bearing central axis indicated by a one-dot chain line in the drawing). Hereinafter, the direction along the central axis is simply referred to as “axial direction”, the direction perpendicular to the central axis is simply referred to as “radial direction”, and the circumferential direction around the central axis is simply referred to as “circumferential direction”. It is called “circumferential direction”.

The inner ring 1 is an annular bearing part having a conical raceway surface 5, a small brim portion 6, and a large brim portion 7 on the outer periphery.

The outer ring 2 is an annular bearing part having a conical raceway surface 8 on the inner periphery and cage guide surfaces 9 and 10 for guiding the cage 4 in the radial direction. The cage guide surfaces 9 and 10 are provided only on the inner periphery of the outer ring 2. The cage guide surface 9 is formed on the inner diameter small diameter side of the inner circumference of the outer ring 2 with the raceway surface 8 as a boundary, and the cage guide surface 10 is formed on the opposite inner diameter large diameter side. The cage guide surfaces 9 and 10 have a conical shape that forms the same surface as the raceway surface 8.

The roller 3 is a tapered roller that is in rolling contact with the raceway surface 5 of the inner ring 1 and the raceway surface 8 of the outer ring 2. In the first embodiment, the single-row tapered roller bearing is exemplified, but an appropriate type of roller bearing such as a cylindrical roller bearing or a double-row roller bearing may be used.

The inner ring 1, the outer ring 2 and the roller 3 are usually made of steel. Examples of the steel include high carbon chrome bearing steel and bare steel.

In the roller bearing according to the first embodiment, an inner ring assembly is constituted by the inner ring 1, the plurality of rollers 3 and the cage 4.

The retainer 4 includes a retainer body 11 that is integrally formed, and a first ring 12 and a second ring 13 that are attached to the outer periphery of the retainer body 11.

The retainer body 11 is formed with a first annular portion 14, a second annular portion 15, and a column portion 17 that divides the

annular portions

14 and 15 into pockets 16. The first annular portion 14 and the second annular portion 15 are continuous over the entire circumference in the circumferential direction. The outer diameter of the second annular portion 15 is set larger than that of the first annular portion 14. On the outer periphery of the first annular portion 14 and the outer periphery of the second annular portion 15, grooves for use in fixing the corresponding first ring 12 or second ring 13 are formed over the entire circumference in the circumferential direction. The pocket 16 is a space for accommodating the rollers 3. The column parts 17 exist at equal intervals in the circumferential direction.

The first ring 12 has a guided surface 18 that is guided in the radial direction by a cage guide surface 9 formed on the small inner diameter side of the outer ring 2. The second ring 13 has a guided surface 19 that is guided in the radial direction by the cage guide surface 10 formed on the inner diameter / large diameter side of the outer ring 2. Each of the first ring 12 and the second ring 13 has the illustrated cross-sectional shape over the entire circumference in the circumferential direction.

The first ring 12 and the second ring 13 are forcibly fitted in the grooves of the corresponding first annular portion 14 or second annular portion 15 in the respective inner peripheral portions. By this fitting, the first ring 12 and the second ring 13 are positioned in the axial direction and the radial direction with respect to the corresponding first annular portion 14 or second annular portion 15. The first ring 12 and the second ring 13 are prevented from rotating in the circumferential direction with respect to the corresponding first annular portion 14 or second annular portion 15. This circumferential detent means may be performed by an appropriate means such as welding or an interference fit to the groove. The first ring 12 and the second ring 13 are fixed to the outer periphery of the corresponding first annular portion 14 or the second annular portion 15 by the positioning and rotation prevention described above.

The guided surface 18 and the guided surface 19 exist on the outer periphery of the corresponding first ring 12 or second ring 13 over the entire circumference in the circumferential direction. The guided surface 18 and the guided surface 19 are surfaces having an angle θ1 with respect to the axial direction on arbitrary virtual planes including the central axes of the cage 4 and the outer ring 2, respectively. The axial width of each of the guided surface 18 and the guided surface 19 extends over the entire width of the corresponding first ring 12 or second ring 13. On the other hand, the cage guide surface 9 and the cage guide surface 10 that are coplanar with the raceway surface 8 of the outer ring 2 are axially arranged on an arbitrary virtual plane including the central axis of the cage 4 and the outer ring 2, respectively. The surface has an angle θ2. The angle θ1 and the angle θ2 are set to the same angle. For this reason, the cage guide surface 9 and the guided surface 18 and the cage guide surface 10 and the guided surface 19 are parallel to each other on the above-described virtual plane, and are in surface contact with each other in a conical shape. It is possible.

The radial clearances between the guided surface 18 and the cage guide surface 9 and between the guided surface 19 and the cage guide surface 10 are set to the same value, and the guide between the cage 4 and the outer ring 2 is set. It corresponds to the clearance. The contact between the roller 3 and the column portion 17 does not contribute to guiding the cage 4 in the radial direction.

The cage 4 includes a cage body 11, a first ring 12, and a second ring 13, and does not have a portion facing both sides defining the width of the outer ring 2 in the axial direction. For this reason, the roller bearing according to the first embodiment can be arranged in either a front combination or a back combination, and in either combination, it is possible to apply preload by arbitrarily using both side surfaces of the outer ring 2. .

The cage body 11 is made of steel. Examples of the steel include cold or hot rolled steel, carbon steel for mechanical structure, stainless steel, nickel / chromium / molybdenum steel, and the like.

The cage body 11 is made of a steel plate having a thickness capable of forming a basic overall shape by pressing, and is formed by a general manufacturing method of a cage punching cage. The aforementioned groove is formed by punching after the aforementioned pressing. In addition, the manufacturing method of the cage main body 11 may employ an appropriate processing means such as pressing, milling, or molding depending on the shape and material of the cage main body 11.

Other materials other than steel may be adopted as a material for forming the cage body 11. For example, the cage body 11 may be formed of resin or high-strength brass. During the bearing operation, the rolling surface of the roller 3 usually contacts either of the column portions 17 located on both sides in the circumferential direction of the roller 3 while rolling on the raceway surfaces 5 and 8. When emphasizing the prevention of wear of the column portion 17 due to the normal contact, it is preferable that the normal contact portion in the column portion 17 is formed of a material that is as excellent in self-lubricity as possible. If the pillar part 17 is formed of resin or high-strength brass, the slidability of the normal contact part in the pillar part 17 can be improved.

The above-mentioned high-strength brass is an alloy obtained by adding 2.0% by mass or less of aluminum, 3.0% by mass or less of manganese, and 1.5% by mass or less of iron to brass of 55.0 to 60.5% by mass of copper. Say.

Examples of the resin include polyamide (PA), polyacetal (POM), polycarbonate (PC), polyethylene terephthalate (PET), polybutylene terephthalate (PBT), polyether ether ketone (PEEK), polyphenylene sulfide ( Engineering plastics or super engineering plastics such as PPS), polytetrafluoroethylene (PTFE), polysulfone (PSF), polyethersulfone (PES), polyimide (PI), polyetherimide (PEI), PA46 + GF, PA66 + GF, etc. Examples thereof include glass fiber reinforced resin.

During the bearing operation, the rolling surface of the roller 3 comes into contact with either of the column portions 17 positioned on both sides in the circumferential direction of the roller 3 while rolling on the raceway surfaces 5 and 8. When emphasizing the prevention of wear of the column portion 17 due to this normal contact, it is preferable that the contact portion of the column portion 17 with the roller 3 is made of a material having an excellent self-lubricity as much as possible. If the column part 17 is formed of resin or high-strength brass, the wear of the column part 17 due to normal contact can be prevented as compared with steel.

On the other hand, the first ring 12 and the second ring 13 are each integrally formed of a resin material. Since the guided surface 18 and the guided surface 19 are each made of the resin material described above, they have a lower coefficient of friction than the surface of the steel cage body 11.

The resin material may be any material as long as it can form the guided surfaces 18 and 19 having a lower coefficient of friction than the surface of the cage body 11, and is preferably excellent in self-lubricity as much as possible. Examples of resin materials having good self-lubricating properties include polyamide (PA), polyacetal (POM), polybutylene terephthalate (PBT), polyetheretherketone (PEEK), polytetrafluoroethylene (PTFE), and the like. .

Further, as a material for forming the first ring 12 and the second ring 13, a sintered material containing a solid lubricant may be adopted. This kind of sintered material also exhibits good self-lubricating properties. Therefore, the guided surfaces 18 and 19 made of the surface of this kind of sintered material have a lower coefficient of friction than the surface of the steel cage body 11.

Examples of the above-mentioned sintered material include those containing graphite. In the case of graphite, it is possible to obtain a sintered material excellent in self-lubricity by increasing the blending amount of graphite in the sintered material as graphite powder having high fluidity. As such a sintered material, for example, a raw material powder containing graphite powder and metal powder is molded in a mold and then sintered, and the granulated powder is used as the graphite powder and sintered. The ratio of free graphite on the surface of the material is 25% to 80% in area ratio, the average particle size of the granulated powder is 60 μm to 500 μm, and the blending ratio of the granulated powder in the raw material powder is 3% to 15% by weight. (This sintered material is disclosed in Japanese Patent Laid-Open No. 2014-25527, and a detailed description thereof is omitted.)

An example of a planetary reduction gear provided with a roller bearing according to the first embodiment is shown in FIGS. As shown in the figure, this planetary speed reducer includes a planetary rotating body 105 as a planetary gear meshing with both

gears

102 and 104 between a sun gear 102 attached to the input shaft 101 and an internal gear 104 fixed to the housing 103. Are arranged, and each planetary rotator 105 is rotatably supported by the carrier 107 connected to the output shaft 106, and the planetary rotator 105 revolves while rotating between the sun gear 102 and the internal gear 104. The revolving motion is output to the output shaft 106 via the carrier 107. A pair of roller bearings 100 according to the first embodiment are disposed between the planetary rotating body 105 and the carrier 107 provided in the planetary reduction gear. The outer ring 2 of each rolling bearing 100 is attached to the planetary rotator 105 and rotates integrally with the planetary rotator 105. The inner ring 1 of each rolling bearing 100 is attached to a support shaft 108 provided on the carrier 107 and is stationary with respect to the outer ring 2.

The roller bearing 100 is given a preload for making the bearing internal clearance negative. Since the roller bearing 100 supports the planetary rotator 105 without play, the movement of the planetary rotator 105 is stabilized, and normal meshing between the planetary rotator 105 and the sun gear 102 or the internal gear 104 can be ensured. . In addition, although the back combination was illustrated as arrangement | positioning of a pair of roller bearing 100, you may make it a front combination. Moreover, although the case where the preload is applied to the inner ring 1 of the roller bearing 100 has been illustrated, the preload may be applied to the outer ring regardless of the combination of the rear surface and the front surface.

The planetary speed reducer shown in the figure performs the first speed reduction of the final speed reducer provided inside the wheel rim of the super large dump truck. The super large dump truck is intended for mines and has a load capacity of 300 t or more. The inventors of the present application have examined the usage environment of the final ultra-high dump final reduction gear. As a result, the roller bearing 100 revolving around the sun gear 102 has a revolving diameter of about 500 mm and a revolving speed of about 500 rpm. The rotation speed was about 1300 rpm, and the maximum centrifugal acceleration was about 75G. When such strong centrifugal acceleration is applied, the lubricating oil inside the bearing becomes dilute in the load region, and the tendency to deviate to the opposite side in the circumferential direction from the load region is remarkable.

As shown in FIG. 1, the roller bearing according to the first embodiment is provided with cage guide surfaces 9 and 10 on the inner circumference of the outer ring 2 and guided

surfaces

18 and 19 on the outer circumference of the cage 2. Therefore, as shown in FIGS. 2 and 3, in the support application of the planetary rotating body 105 provided in the planetary speed reducer, the cage 4 is guided in the radial direction by the inner circumference of the outer ring 2 that rotates integrally with the planetary rotating body 105. Is done. For this reason, compared with the case where the cage 4 is guided by the inner ring 1, between the guided surface 18 and the cage guiding surface 9 and between the guided surface 19 and the cage guiding surface 10 shown in FIG. 1. The relative speed difference (V) between them becomes small, and the circumferential lengths of the cage guide surfaces 9 and 10 and the guided surfaces 18 and 19 become long and the contact surface pressure (P) becomes low. In particular, in the support application of the planetary rotating body 105 as shown in FIGS. 2 and 3, the lubricating oil moves to the inner peripheral side of the outer ring 2 by the action of a large centrifugal force accompanying the revolution movement of the planetary rotating body 105. 1 is easily supplied to the cage guide surfaces 9 and 10 and the guided surfaces 18 and 19 shown in FIG. 1, and the lubricity of the cage guide surfaces 9 and 10 and the guided surfaces 18 and 19 is improved. Due to the suppression of the PV value and the lubricity, wear and seizure of the guided surfaces 18 and 19 and the cage guide surfaces 9 and 10 are prevented.

Furthermore, in the roller bearing according to the first embodiment, the guided surface 18 of the first ring 12 and the guided surface 19 of the second ring 13, which are separate parts fixed to the cage body 11, are on the surface of the cage body 11. Since the friction coefficient is lower than that of the guide surfaces 18, 19, the cage guide surfaces 9, 10 and the guided surfaces 18, 19 are further prevented from being worn and seized. By preventing the cage guide surfaces 9 and 10 and the guided surfaces 18 and 19 from being worn, it is possible to prevent the guide 4 from rolling and guide the rolling element 4 and prevent the column portion 17 from wearing abnormally. Also become.

In addition, the roller bearing according to the first embodiment includes the contact between the guided surface 18 and the cage guiding surface 9 on both sides in the axial direction of the cage 4 with the pocket 16 as a boundary, and the guided surface 19 and the cage guiding surface. 10 can be contacted, so that the tilt of the cage 4 can be suppressed even when a large centrifugal force due to the revolving motion of the planetary rotating body 105 shown in FIGS. 2 and 3 acts on the cage 4. As a result, a decrease in the contact area between the guided surface 18 and the cage guide surface 9 and a decrease in the contact area between the guided surface 19 and the cage guide surface 10 can be suppressed, and an abnormality between the

column portion

17 and 3. Therefore, wear and seizure of the guided surfaces 18 and 19 and the cage guide surfaces 9 and 10 are further prevented, and abnormal wear of the column portion 17 is further prevented.

As described above, the roller bearing according to the first embodiment, as shown in FIGS. 2 and 3, even when supporting the planetary rotating body 105 provided in the planetary reduction gear, the guided surface of the cage 4 shown in FIG. 1. 18 and 19 and the cage guide surfaces 9 and 10 of the outer ring 2 are suppressed, and the lubricity of the guided surfaces 18 and 19 of the cage 4 and the cage guide surfaces 9 and 10 of the outer ring 2 is improved. Thus, it is possible to improve the slidability on the guided surfaces 18 and 19 of the cage 4 and to suppress the inclination of the cage 4 when the

cage guiding surfaces

9 and 10 and the guided surfaces 18 and 19 are in contact with each other. Therefore, it is possible to prevent wear and seizure of the cage guide surfaces 9 and 10 and the guided surfaces 18 and 19 which are cage guide portions, and to prevent abnormal wear of the column portion 17 of the cage 4.

In the roller bearing according to the first embodiment, the guided surfaces 18 and 19 and the

cage guiding surfaces

9 and 10 are parallel to each other on a virtual plane including the central axis of the cage 4 and the outer ring 2 arranged coaxially. Since it has a surface shape, it is possible to prevent wear by making the contact mode between the guided surface 18 and the cage guide surface 9 and the contact mode between the guided surface 19 and the cage guide surface 10 into a surface contact.

In the roller bearing according to the first embodiment, the first ring 12 and the second ring 13 are each formed of a resin material or a sintered material containing graphite. Can have a self-lubricating property.

In the roller bearing according to the first embodiment, the first ring 12 and the second ring 13 are present only in a region opposed to the inner circumference of the outer ring 2 in the radial direction. Can be replaced with existing roller bearings.

In the first embodiment, the raceway surface 8 of the outer ring 2 and the cage guide surfaces 9 and 10 are the same surface, but the raceway surface 8 and the cage guide surface may be different surfaces. In the first embodiment, the first ring 12 and the second ring 13 are each formed of a single material and the entire ring has a lower coefficient of friction than the surface of the cage body 11, but at least the guided surface 18, It is only necessary to use a low friction coefficient in the portion 19 and the portion to be the guided surface of the ring and the remaining annular portion may be formed of different materials, and the ring portion may improve the mechanical strength of the ring. . FIG. 4 shows a second embodiment as an example. In the following, only differences from the first embodiment will be described.

As shown in the figure, the roller bearing according to the second embodiment is formed with cylindrical retainer guide surfaces 21 and 22 on the inner periphery of the outer ring 20, and the first ring 31 and the second ring 32 of the retainer 30. Cylindrical guided surfaces 33 and 34 are formed. These cylindrical surface central axes coincide with the central axis of the outer ring 20 and the central axis of the cage 30. The guided surfaces 33 and 34 and the cage guide surfaces 21 and 22 do not have an angle with respect to the axial direction on a virtual plane including the central axis of the cage 30 and the outer ring 20 arranged coaxially. For this reason, when the guided surfaces 33 and 34 and the corresponding cage guide surface 21 or the cage guide surface 22 come into contact with each other in the direction of the centrifugal force, no axial component force is generated, and the cage 30 is reliably Guided.

The first ring 31 and the second ring 32 have

ring bodies

35 and 36 each formed in an annular shape from steel. The ring body portion 35 and the ring body portion 36 have a cylindrical inner surface and an outer surface, respectively.

The guided surface 33 and the guided surface 34 are each composed of a surface treatment layer fixed so as to cover the outer peripheral surface of the corresponding ring body portion 35 or the ring body portion 36. This surface treatment is for improving the slidability of the guided surfaces 33 and 34 as compared with the surfaces of the

ring bodies

35 and 36 and the surface of the cage main body 37, and preferably has excellent self-lubricity as much as possible. . As the surface treatment, one having a lower friction coefficient than the surface of the cage body 37 is particularly preferable, and examples thereof include fluorine resin coating, molybdenum coating, DLC coating, ceramic coating, and hard chrome plating.

In the drawing, the thickness of the surface treatment layer forming the guided surfaces 33 and 34 is exaggerated. A substantially entire area in the radial direction of the first ring 31 and the second ring 32 is constituted by the corresponding ring body portion 35 or the ring body portion 36. For this reason, the mechanical strength of each of the first ring 31 and the second ring 32 is substantially set by the corresponding ring body portion 35 or the ring body portion 36.

On the other hand, the cage body 37 is made of resin or high-strength brass. For this reason, when the pillar part of the cage body 37 abnormally contacts the roller 3, the aggressiveness of the cage body 37 against the roller 3 is lower than that of the same-shaped cage body made of steel. Instead, the rigidity with respect to the deformation of the cage body 37 is inferior to that of the same shape cage body made of steel.

The elastic modulus of steel, which is the material forming the ring body portion 35 of the first ring 31 and the ring body portion 36 of the second ring 32, is compared to the resin material or sintered material that is the material forming the cage body 37. Is expensive. That is, the first ring 31 and the second ring 32 are formed in an annular shape from a material having a higher elastic modulus than the material of the cage body 37 in the corresponding ring body part 35 or ring body part 36, respectively. For this reason, compared with the case where the cage having the same shape as the cage 30 is formed only from the material of the cage body 37, the rigidity against deformation of the cage 30 is improved by the first ring 31 and the second ring 32. ing.

Centrifugal force due to the revolving motion of the planetary rotating body acts on the cage 30, the guided surface 33 of the first ring 31 contacts the cage guiding surface 21 of the outer ring 20, and the guided surface 34 of the second ring 32 When the cage guide surface 22 comes into contact, the cage 30 undergoes elliptical deformation such that its diameter decreases in the direction in which the centrifugal force acts. At this time, a pocket in which the pocket clearance is reduced is generated in the cage body 37 that is elliptically deformed. In the second embodiment, as described above, the rigidity with respect to the deformation of the cage 30 is improved by the first ring 31 and the second ring 32, so that the above-described elliptical deformation is suppressed, and as a result, the cage body 37 Abnormal wear of the column is prevented.

Thus, the roller bearing according to the second embodiment has a PV value between the guided surfaces 33 and 34 of the cage 30 and the cage guide surfaces 21 and 22 of the outer ring 20 even when the planetary rotor is supported. To suppress, improve the lubricity of the guided surfaces 33 and 34 of the cage 30 and the cage guide surfaces 21 and 22 of the outer ring 20, improve the slidability on the guided surfaces 33 and 34 of the cage 4, Furthermore, since the elliptical deformation and inclination of the cage 30 at the time of contact between the cage guide surfaces 21 and 22 and the guided surfaces 33 and 34 can be suppressed, the cage guide surface 21 is further improved than in the first embodiment. , 22 and guided

surfaces

33, 34 can be prevented from being worn and seized, and abnormal wear of the column portion of the cage 30 can be prevented.

In the roller bearing according to the second embodiment, the first ring 31 and the second ring 32 have

ring bodies

35 and 36 each formed in an annular shape by steel, and the guided surfaces 33 and 34 are the rings. Since it consists of a surface treatment layer applied to the

body portions

35 and 36, the first ring 31 and the second ring 32 improve the rigidity against the elliptical deformation of the cage 30, and excellent sliding on the guided surfaces 33 and 34. Can have sex.

In the first embodiment and the second embodiment, the guided surface is provided over the entire outer periphery of the first ring and the second ring, but the guided surface may be provided intermittently in the circumferential direction. As an example, FIG. 5 shows a roller bearing according to a third embodiment.

As illustrated, in the cage 40 according to the third embodiment, the outer circumference of the first ring 42 and the outer circumference of the second ring 43 fixed to the cage body 41 and the inner circumference of the outer ring 2 are set. The gap widths in the radial direction are different at regular intervals in the circumferential direction. FIG. 5 shows a side surface of the roller bearing according to the third embodiment on the first ring 42 side, but the above-described gap width change in the second ring 43 is common to the first ring 42. Hereinafter, details will be described by taking the first ring 42 side as an example.

As shown in FIG. 6, the first ring 42 has protrusions 44 protruding in the radial direction at equal intervals in the circumferential direction. The guided surface 45 is provided at the distal end of the protruding portion 44 in the radial direction. Of the first ring 42, the outer peripheral portion between the protrusions 44 adjacent in the circumferential direction is an intermediate surface 46 having an outer diameter smaller than the guided surface 45 over the entire axial width of the first ring 42. ing. Therefore, as shown in FIG. 5, the radial width of the gap g set between the intermediate surface 46 and the inner periphery of the outer ring 2 is set between the guided surface 45 and the inner periphery of the outer ring 2. It becomes larger than the guide clearance. For this reason, the lubricating oil is less likely to enter the above-described guide gap, and more easily enters the gap g. That is, the oil permeability that crosses between the outer periphery of the first ring 42 and the inner periphery of the outer ring 2 in the axial direction is improved by the gap g.

The pitch in the circumferential direction of the protrusions 44 and the pitch in the circumferential direction of the rollers 3 by the cage 40 are the same. That is, the protrusion 44 exists only in the circumferential range facing the end surface of the roller 3 in the axial direction. The space between the rollers 3 adjacent in the circumferential direction inside the bearing is opened from the gap g in the axial direction toward the outside of the bearing. The opening area is not reduced by the protrusion 44 because the protrusion 44 does not protrude in the circumferential direction with respect to the end face of the roller 3. For this reason, the protrusion part 44 does not prevent the lubricating oil from flowing into the space between the rollers 3 described above.

As described above, the roller bearing according to the third embodiment has the protruding portions 44 that the first ring 42 and the second ring 43 protrude in the radial direction at circumferential intervals corresponding to the rollers 3, respectively. Since the surface 45 is provided on the protrusion 44, the protrusion 44 prevents the inflow of lubricating oil into the space between the rollers 3 adjacent in the circumferential direction by the gap g between the protrusions 44 adjacent in the circumferential direction. The oil permeability between each of the first ring 42 and the second ring 43 and the inner periphery of the outer ring 2 can be improved.

The fourth embodiment will be described with reference to FIG. The roller bearing according to the fourth embodiment is different from the roller bearing according to the first to third embodiments in that the bearing type is changed from a tapered roller bearing to a cylindrical roller bearing. The outer ring 50 has

collars

51 and 52 on both sides in the axial direction. The cage guide surfaces 53 and 54 are formed in cylindrical shapes on the inner circumferences of the corresponding

collars

51 and 52, respectively. The cage guide surfaces 53 and 54 have the same diameter. The first annular portion 61 and the second annular portion 62 of the cage main body 60 have the same shape, and the first ring 63 and the second ring 64 have the same shape. The guided surface 65 formed on the first ring 63 and the guided surface 66 formed on the second ring 64 are along the axial direction (angle 0 ° with respect to the axial direction) on the above-described virtual plane. For this reason, the guided surfaces 65 and 66 and the cage guide surfaces 53 and 54 are parallel to each other on the above-described virtual plane.

The fifth embodiment will be described with reference to FIG. The roller bearing according to the fifth embodiment is different from the roller bearing according to the first to third embodiments in that the bearing type is changed from a tapered roller bearing to a self-aligning roller bearing. The outer ring 70 has a spherical track 71 corresponding to the

spherical rollers

81 and 82 on the inner periphery. The cage main body 90 has a pair of first annular portions 91 that define the cage width, and a second annular portion 92 that is positioned at the center of the cage width. A space between each of the first

annular portions

91 and 91 and the second annular portion 92 is divided into pockets by a pillar portion 93. A first ring 94 is fixed to each of the first

annular portions

91, 91, and a second ring 95 having an outer diameter larger than that of the first ring 94 is fixed to the second annular portion 92. Of the inner periphery of the outer ring 70, cage guide surfaces 72, 72 for guiding the guided surface 96 formed on the first ring 94 are formed on the inner periphery of the spherical track 71 extending in the axial direction. . The axial center portion of the spherical track 71 that does not contact the double-row

spherical rollers

81 and 82 is a cage guide surface 73 that guides a guided surface 97 formed on the second ring 95. The guided surface 96 is along a cage guide surface 72 that is flush with the spherical track 71 on the virtual plane, and the guided surface 97 is included in the spherical track 71 on the virtual plane. Along the vessel guide surface 73. For this reason, the guided surfaces 96 and 97 and the cage guide surfaces 72 and 73 are parallel to each other on the above-described virtual plane.

The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. Accordingly, the scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

1

Inner ring

2, 20, 50, 70 Outer ring 3

Rollers

4, 30, 40

Cage

9, 10, 21, 22, 53, 54, 72, 73

Cage guide surface

11, 37, 41, 60, 90

Cage body

12, 31, 42, 63, 94

First ring

13, 32, 43, 64, 95

Second ring

14, 61, 91 First

annular portion

15, 62, 92 Second annular portion 16

Pocket

17, 93 Column 18 19, 33, 34, 45, 65, 66, 96, 97

Guide surface

35, 36 Ring body 44 Projection

Claims

In a roller bearing comprising an inner ring, an outer ring, a plurality of rollers interposed between the inner ring and the outer ring, and a cage that holds these rollers,
The retainer has a retainer body formed integrally, a first ring and a second ring fixed to the retainer body,
A first annular part, a second annular part, and a pillar part that divides the two annular parts into pockets are formed in the retainer body,
The first ring is fixed to the first annular portion;
The second ring is fixed to the second annular portion;
A cage guide surface for guiding the cage in the radial direction is provided only on the inner periphery of the outer ring,
Of the cages, guided surfaces guided by the cage guide surfaces are provided on the first ring and the second ring,
The roller bearing characterized in that the guided surface has a lower coefficient of friction than the surface of the cage body.
In a roller bearing comprising an inner ring, an outer ring, a plurality of rollers interposed between the inner ring and the outer ring, and a cage that holds these rollers,
The retainer has a retainer body formed integrally, a first ring and a second ring fixed to the retainer body,
A first annular part, a second annular part, and a pillar part that divides the two annular parts into pockets are formed in the retainer body,
The first ring is fixed to the first annular portion;
The second ring is fixed to the second annular portion;
A cage guide surface for guiding the cage in the radial direction is provided only on the inner periphery of the outer ring,
Of the cages, guided surfaces guided by the cage guide surfaces are provided on the first ring and the second ring,
The roller bearing, wherein the first ring and the second ring are each formed in an annular shape from a material having a higher elastic modulus than the material of the cage body.
The roller bearing according to claim 1, wherein the first ring and the second ring are each formed in an annular shape from a material having a higher elastic modulus than the material of the cage body.
4. The guide surface according to claim 1, wherein the guided surface and the cage guide surface are parallel to each other on a virtual plane including a central axis of the cage and the outer ring arranged coaxially. The roller bearing described in the item.
The first ring and the second ring each have a protrusion protruding in the radial direction at a circumferential interval corresponding to the roller;
The roller bearing according to claim 1, wherein the guided surface is provided on the protrusion.
The roller bearing according to any one of claims 1 to 5, wherein the cage body is made of steel, resin, or high-strength brass.
The roller bearing according to any one of claims 1 to 6, wherein the first ring and the second ring are each formed of a resin material or a sintered material containing graphite.
Each of the first ring and the second ring has a ring body portion formed in an annular shape by steel,
The roller bearing according to any one of claims 1 to 6, wherein the guided surface includes a surface treatment layer applied to the ring body portion.
The roller bearing according to any one of claims 1 to 8, wherein the roller bearing is disposed between a planetary rotating body and a carrier provided in the planetary reduction gear.