JP4636035B2 - Rolling bearing - Google Patents

Description

  The present invention relates to a rolling bearing, and more particularly to a rolling bearing used at high speed rotation, such as a drive motor for a general industrial machine or a machine tool, or a main spindle for a machine tool.

  In recent years, motors with very high rotational speed have appeared in drive motors used in general industrial machines and machine tools. This tendency is particularly strong in machine tool applications as the machine tool spindle speed increases.

If the spindle speed of the machine tool is increased to some extent (for example, the rotational speed of the spindle is about 10,000 min ⁻¹ or less), a drive motor having a maximum rotational speed of about 5,000 to 8,000 min ⁻¹ is used. The speed can be increased by using a gear or a belt. However, when the rotational speed of the main shaft is 15,000 to 20,000 min ⁻¹ , the speed increasing ratio is more than twice, and in order to transmit a certain amount of driving force, the gear diameter and the belt wheel diameter also increase. The peripheral speed of the transmission part becomes very large. As a result, gear engagement noise and tooth wear and chipping are likely to occur in gear drive, and belt slippage, flapping, wear, belt breakage, and the like are likely to occur in belt drive. Further, in order to prevent the belt from slipping or flapping during high-speed rotation, the belt tension must be increased, and the motor support bearing is easily damaged due to overload.

  For these reasons, the driving method of the machine tool spindle has been changed from gear driving or belt driving to a direct driving method by coupling. In the case of the coupling direct drive system, the driving torque is transmitted directly to the main shaft side through the coupling, so that no load component due to the driving force is generated in the motor support bearing. However, since the rotational speed of the motor is the same as that of the main shaft, a rolling bearing for high-speed rotation corresponding to this has become necessary.

For example, in a conventional deep groove ball bearing, various cages are employed depending on the number of rotations (see, for example, Patent Documents 1 and 2). In a general 4-pole or 2-pole general-purpose motor (1,500 to 3,600 min ⁻¹ ), as shown in FIG. 10, an iron cage 100 by press molding having a spherical pocket 101 is employed. On the other hand, in the case of a medium to high speed motor (about 5,000 to 8,000 min ⁻¹ ), as shown in FIG. 11, the pocket 111 has a spherical shape and is made of a synthetic resin with excellent wear resistance. A vessel 110 is employed.

  As shown in FIG. 12, in Patent Document 1, the inner surface of the pocket 121 is formed in a cylindrical shape for the purpose of improving the friction resistance and wear characteristics and preventing the cage noise during rotation, and a convex portion is formed on a part of the pocket 121. A ball guide resin cage 120 that is employed in a high-speed deep groove ball bearing provided with 122 is devised.

Furthermore, as shown in FIG. 13, in Patent Document 2, as in the case of the iron press cage 100, a structure in which two synthetic resin cage members 132 having corrugated pocket portions 131 are axially opposed to each other is combined. A cage 130 is also devised.
JP-A-9-158951 (FIG. 3) JP 2006-17301 (FIG. 4)

  By the way, in the resin cage 130 shown in FIG. 13, the friction resistance and wear characteristics of the pocket surface are improved as compared with iron, but the cross-sectional thickness of the claw portion 133 of the fitting portion that combines the two cage members 132 is combined. The claw portion 133 is formed by a high-frequency vibration load acting on the cage 130 at a high speed rotation and a repeated load received from the ball, because the cross-sectional thickness around the hole portion 134 into which the claw portion 133 is inserted facing the claw portion 133 is thin. Problems such as cracks and breakage due to stress concentration in the vicinity of the roots and the edge portions of the holes 134 are extremely likely to occur. Even if it is attempted to increase the strength of these fitting portions, there is not enough space to increase the thickness around the claw portion 133 and the hole portion 134.

  Further, in the case of the iron cage 100 as shown in FIG. 10, the two cage members 102 are caulked with metal rivets 103, so that the strength of the caulking portion is large even at high speed rotation, while the iron cage 100 is made of iron. Therefore, the pocket inner surface is worn out.

Further, in the case of a high-speed motor having a rotational speed of 15,000 to 20,000 min ⁻¹ or more required from the above background, the dmn value (dm: of the rolling bearing) of the motor support bearing The rolling element pitch circle diameter (mm), n: number of rotations (min ⁻¹ )) exceeds 800,000 to 1,000,000, and the cage expands radially outward due to centrifugal force during rotation. For this reason, the following problems may occur in the cages 110 and 120 shown in FIGS.

The retainers 110 and 120 shown in FIGS. 11 and 12 are so-called ball guide retainers. As indicated by ΔR _{1 to} ΔR ₃ , the radial movement amounts of the crown-shaped retainers 110 and 120 having a single annular ring structure are as follows. , The clearance between the balls 112 and 123 and the pockets 111 and 121 holding the balls 112 and 123 is restricted.

  For example, in the case of the cage 120 in FIG. 12, the contact position between the ball 123 and the cage 120 is the width A of the convex portion 122 in the low-speed rotation region where the centrifugal force deformation is small. However, in the case of the high-speed rotation region, since the pillar portion 124 of the cage 120 is supported by the annular portion 125 only on one side, as shown in FIG. The convex portion 122 is inclined in the outer diameter direction by an angle β simultaneously with the outer diameter surface and inner diameter surface of the cage from the column portion 124 toward the column portion 124.

  As a result, the contact portion with the ball 123 is biased toward the tip end side of the pillar portion 124 and becomes in an uneven contact state, and finally the contact portion is limited to the tip end side, and the contact surface pressure P increases. Further, in the case of high-speed rotation, since the sliding speed V between the ball 123 and the pocket contact portion is large, as a result, the PV value of the contact portion increases, and deformation, wear and melting of the cage 120 due to local heat generation occur. There was a problem.

In addition, as shown in FIGS. 11 (b) and 12 (d), when a portion in contact with the balls 112, 123 is provided on the pocket inner diameter side, the guide clearance is reduced by the centrifugal force expansion of the cages 110, 120. , in some cases, the guide gap ([Delta] R 2 in FIG. 11 _(b), FIG. 12 [Delta] R 3 in _(d)) becomes 0 or less to restrain the ball in the contact portion, even possibly causing with poor rotation and baked there were.

  In order to reduce the inclination due to the centrifugal force, the cross-sectional areas of the annular portions 113 and 125 are increased, that is, the axial thickness (see L in FIG. 12C) and the radial thickness of the annular portions 113 and 125. (Refer to H in FIG. 12 (c)).

  Further, when the inclination angle β due to the centrifugal force at the time of high-speed rotation was calculated for the conventional crown-shaped resin cage having a single annular ring structure, the dmn value of the bearing was 90, although there was a difference depending on the shape of the cage and the dmn value. It was found that an inclination of about 1 ° to 4 ° occurred at 10,000 or more.

  For this reason, the crown resin holders 110 and 120 having a single ring ring structure with an integrated structure, which has higher cage strength than the synthetic resin holder 130 made of a combination of two cage members, are in the conventional specifications. On the other hand, there has been a demand for a rolling bearing that does not cause pocket wear or damage during further high-speed rotation, and that provides stable rotation characteristics.

  Therefore, the present invention has been made in view of the above circumstances, and its purpose is to employ a synthetic resin cage with a single annular ring structure, even under high-speed rotation conditions in which deformation due to centrifugal force occurs. An object of the present invention is to provide a rolling bearing capable of obtaining stable rotational characteristics without causing abnormal temperature rise or seizure.

The above object of the present invention is achieved by the following configurations.
(1) An annular part and a plurality of cantilever pillars extending from one side surface of the annular part are provided, and each pillar is formed by the annular part and the adjacent pillar part. A rolling bearing comprising a synthetic resin cage that accommodates a moving body in a freely rolling manner,
The column portion has a guide portion that is guided by contact with the rolling element,
The column portion and the guide portion are inclined inward in the radial direction from the annular portion toward the tip end portion of the column portion in order to correct inclination due to deformation of the column portion due to centrifugal force during bearing rotation. The rolling bearing is characterized in that the inclination angle corresponds to an angle at which the column portion is deformed radially outward by the centrifugal force .
( 2 ) The rolling bearing according to (1) , wherein the rolling element is a ball.
( 3 ) The rolling bearing according to (1) , wherein the rolling element is a cylindrical roller.
(4) The rolling bearing according to any one of (1) to (3), wherein the dmn value is 900,000 or more.

  According to the rolling bearing of the present invention, a cage made of synthetic resin having a single annular ring structure is employed, and the cage is inclined radially inward from the annular portion toward the tip portion of the column portion. The tilt of the cage is corrected under high-speed rotation conditions in which deformation due to centrifugal force occurs, and stable rotation can be obtained without causing abnormal temperature rise or seizure.

  Hereinafter, rolling bearings according to embodiments of the present invention will be described in detail with reference to the drawings.

(First embodiment)
As shown in FIG. 1, the rolling bearing 10 of the first embodiment is a deep groove ball bearing, an outer ring 11 having an outer ring raceway surface 11 a on an inner peripheral surface, an inner ring 12 having an inner ring raceway surface 12 a on an outer peripheral surface, A ball 13, which is a plurality of rolling elements disposed between the outer ring raceway surface 11 a and the inner ring raceway surface 12 a, and a synthetic resin cage 14 having a single annular ring structure for holding the ball 13, and the ball 13. And a pair of seal members 15 for sealing between the arranged inner and outer rings 11 and 12.

  The retainer 14 includes an annular portion 21 and a plurality of cantilevered column portions 22 extending from one side surface 21 a of the annular portion 21, and is formed by an annular portion 21 and a column portion 22 adjacent to the annular portion 21. The balls 13 are accommodated in the respective pockets 23 so as to roll freely. The inner surface of the pocket 23 formed by the annular portion 21 and the adjacent column portion 22 is formed in a cylindrical shape, and the inner circumferential surface of the radially inner edge of the column portion 22 is formed on the inner surface of the pocket 23. A protruding portion 24 is formed as a guide portion that protrudes and is guided by contact with the ball 13.

  Furthermore, the cage 14 has a structure in which the deformation in the radial direction due to the centrifugal force is taken into consideration in advance in the radial direction inward from the annular portion 21 toward the tip portion of the column portion 22 by the deformation due to the predetermined centrifugal force. The inclination is corrected when it is deformed by centrifugal force during high-speed rotation, and the column portion 22 is substantially horizontal in the axial direction so that the contact position between the ball 13 and the pocket 23 of the cage 14 is appropriate. is there.

  That is, as shown in FIG. 2, a reverse taper is provided inward in the radial direction from the annular portion 21 toward the tip of the column portion 22 in advance by an inclination angle β due to centrifugal force. That is, at the time of non-rotation, the inner peripheral end 22a of the tip of the column part 22 is formed to have a smaller diameter than the inner end 21a of the annular part 21 constituting the pocket 23, and the outer peripheral end 22b of the tip of the post 22 is formed. Is formed to have a smaller diameter than the outer end portion 21b of the annular portion 21 constituting the pocket 23, and the outer end portion 21b of the annular portion 21 is located closer to the distal end side of the column portion 22 than the inner end portion 21a.

  Thereby, the convex part 24 formed in the radial direction inner edge part of the pillar part 22 also inclines in the radial direction toward the front-end | tip part of the pillar part 22. FIG. For this reason, in the low-speed region where deformation does not occur, the ball 13 is in an uneven contact on the base side 24a of the convex portion 24. In this case, since the rotation is low speed and the sliding speed V is small, the PV value of the contact portion is It is small and does not cause problems such as wear, deformation or melting due to large heat generation. Further, if the contact is made in a biased manner, the retainer 14 is more likely to be stabilized when it comes into contact with the base side 24a closer to the axial center of the retainer 14 (near the center of gravity of the retainer) than to the distal end side 24b.

  As materials for the cage 14, polyamide (PA), polyphenylene sulfide (PPS), polyetheretherketone (PEEK), polyimide (PI), polyamideimide (PAI), polyacetal (POM), etc. can be used as required. Further, a fiber-based reinforcing material such as glass fiber (GF), carbon fiber (CF), or carbon nanofiber may be added, or other reinforcing additives may be included. Further, as a method for manufacturing the cage 14, cutting molding, injection molding, or the like is selected.

  Since the amount of centrifugal force deformation varies depending on the strength property value of the material used, it is preferable to use a material having a high strength property value in order to suppress the tilt angle β to some extent as the dmn value of the bearing increases. If the tilt angle is 5 ° or more, the contact between the balls 13 and the pockets 23 at the time of low-speed rotation without deformation may increase and may cause unstable behavior. It is better to increase the strength so that it is less than 0 °, preferably less than 4 °.

  In addition, in the case of an additive, particularly a carbon-based additive, the linear expansion coefficient can be reduced by mixing a large amount.

As shown in FIG. 2C, the clearance ΔR ₃ between the convex portion 24 of the pocket 23 and the ball 13 is reduced by the deformation of the column portion 22 due to the centrifugal force, so that ΔR ₃ <0 does not occur during high-speed rotation. In addition, ΔR ₃ is set large in advance. Furthermore, some resin materials have a large linear expansion coefficient. In this case, ΔR ₃ is set to be larger in advance by adding the amount of expansion in the radial direction of the cage 14 due to the temperature rise during high-speed rotation. It is better to keep it.

  In this way, the amount of radial movement of the cage 14 may be large under low speed conditions where the vibration load during rotation is small. However, during high speed rotation, the column 22 is parallel to the axial direction due to deformation of the column 22 due to centrifugal force. Thus, the amount of movement in the radial direction is reduced, and a uniform contact state between the balls 13 and the pockets 23 of the cage 14 is maintained. As a result, the amplitude at the time of vibration of the cage is suppressed, the collision load applied from the ball 13 to the cage 14 can be reduced, and the stable rotation condition of the cage 14 can be maintained.

  In addition, the structure of the guide part contact-guided by the ball | bowl 13 can be changed suitably. That is, the guide portion may be a single convex portion 24 continuous in the extending direction of the column portion 22 as shown in FIG. 2, but as shown in the first modification of FIG. In addition, a plurality of curved convex portions 25, 25 spaced in the extending direction of the column portion 22 may be used. Moreover, as shown in the 2nd modification of FIG.3 (b), you may be comprised by the several trapezoid convex part 26 and 26 spaced apart in the extension direction of the pillar part 22. As shown in FIG.

Further, as shown in the third modification of FIG. 4, the guide portion is formed on the circumferential side surface of the radially outer edge portion of the column portion 22 by an outer diameter-side convex portion 27 protruding from the inner surface of the pocket 23. May be. In addition, as shown in the fourth modification of FIG. 5, the guide portion is formed on the inner diameter side convex portion 24 formed on the radially inner edge portion of the column portion 22 and on the radially outer edge portion of the column portion 22. Further, it may be constituted by both the outer diameter side convex portions 27. In this case, the clearance ΔR ₄ between the outer-diameter convex portion 27 and the ball 13 when not rotating is smaller than the clearance ΔR ₃ between the inner-diameter convex portion 24 and the ball 13 (ΔR ₄ <ΔR ₃ ) and stopped. If the specifications are such that ΔR ₃ > 0 and ΔR ₄ > 0 during the period from the state to the maximum rotation, if the column part is inclined and deformed by centrifugal force in the process from the low speed rotation to the maximum rotation, the guide unit Is shifted from the convex portion 27 on the outer diameter side to the convex portion 24 on the inner diameter side, the amount of movement of the cage 14 in the radial direction hardly changes, and more stable rotation is obtained.

(Second Embodiment)
Next, a rolling bearing according to a second embodiment of the present invention will be described with reference to FIG. In addition, about the part equivalent to 1st Embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

As shown in FIG. 6, the deep groove ball bearing 10a of the second embodiment is different from that of the first embodiment in the pocket shape of the crown-shaped resin retainer 14a having a single annular ring structure. That is, in the first embodiment, the inner surface of the pocket 23 formed by the annular portion 21 and the adjacent column portion 22 of the retainer 14 is formed in a cylindrical shape. Yes.
Other configurations and operations are the same as those in the first embodiment.

(Third embodiment)
Next, a rolling bearing according to a third embodiment of the present invention will be described with reference to FIG. In addition, about the part equivalent to 1st Embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

  The rolling bearing 30 of the present embodiment is a double-row cylindrical roller bearing, and includes an outer ring 31 having a pair of outer ring raceway surfaces 31a on the inner peripheral surface, an inner ring 32 having a pair of inner ring raceway surfaces 32a on the outer peripheral surface, and an outer ring raceway. Rollers 33, which are a plurality of rolling elements arranged in a row so as to roll freely between the surface 31a and the inner ring raceway surface 32a, and a synthetic resin cage 34 having a pair of single annular rings that hold the rollers 33 in each row. And comprising.

  As shown in FIGS. 7B and 7C, the retainer 34 includes an annular portion 41 and a plurality of cantilever column portions 42 extending from one side surface 41a of the annular portion 41. Rollers 33 are accommodated in rolls 43 in respective pockets 43 formed by the annular portion 41 and the column portion 42 adjacent thereto. A circumferential side surface 42a of the column portion 42 constituting the inner surface of the pocket 43 is formed by a cylindrical surface having a uniform curvature radius R extending in the axial direction.

Also in the present embodiment, the structure is inclined inward in the radial direction by an angle β from the annular portion 41 toward the tip portion of the column portion 42 in advance by the amount of deformation caused by a predetermined centrifugal force, and the centrifugal force during high-speed rotation Thus, the amount of inclination is corrected when deformed, and the column portion 22 becomes substantially horizontal in the axial direction so that the contact position between the roller 33 and the pocket 43 of the cage 34 becomes appropriate. For this reason, the outer peripheral edge part 42b and the inner peripheral edge part 42c of the pillar part 42 constitute a guide part inclined inward in the radial direction, and the amount of radial movement of the cage 34 is the outer peripheral edge part of the pillar part 42 during low-speed rotation. The amount of movement of the cage 34 in the radial direction is restricted by the inner peripheral edge portion 42c of the column portion 42 during high-speed rotation.
Other configurations and operations are the same as those in the first embodiment.

(Fourth embodiment)
Next, a rolling bearing according to a fourth embodiment of the present invention will be described with reference to FIG. In addition, about the part equivalent to 3rd Embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

  As shown in FIG. 8, the double-row cylindrical roller bearing 30a of the fourth embodiment differs from that of the third embodiment in the columnar shape of the crown-shaped resin retainer 34a having a single annular ring structure. That is, in the third embodiment, the circumferential side surface 42a of the column portion 42 of the cage 34 is formed by a cylindrical surface having a uniform radius of curvature R, but the circumferential side surface 42a of the present embodiment is The roller 33 is formed by a cylindrical surface 44a having a radius of curvature R on the radially outer side than the PCD, and is formed by a flat surface 44b continuous from the cylindrical surface 44a on the radially inner side of the PCD. An outer diameter side flat surface 44 c is also formed between the cylindrical surface 44 a and the outer peripheral edge of the column portion 42. Furthermore, the outer peripheral surface of the column part 42 is formed so as to be inclined so that the radial width of the outer-diameter flat surface 44c becomes smaller toward the tip portion.

  By adopting such a cage shape, the pillar portion 42 of the cage 34a is reduced in cross-sectional thickness from the annular portion 41 toward the tip portion, the weight of the cage 34a is reduced, and due to centrifugal force. Expansion of the column part 42 is relieved.

  In the present embodiment, the structure is inclined inward in the radial direction by an angle β from the annular portion 41 toward the tip portion of the column portion 42 in advance by a deformation due to a predetermined centrifugal force. When deformed, the amount of inclination is corrected, the column portion 22 becomes substantially horizontal in the axial direction, and the contact position between the roller 33 and the pocket 43 of the cage 34a becomes appropriate. In this case, the boundary edge 45 between the cylindrical surface 44a and the outer diameter side flat surface 44c of the column portion 42 constitutes a guide portion that is inclined inward in the radial direction, and the amount of radial movement of the cage 34a is high during high-speed rotation. It is regulated by this boundary edge 45.

(Fifth embodiment)
Next, a rolling bearing according to a fifth embodiment of the present invention will be described with reference to FIG. In addition, about the equivalent part to 4th Embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

  The rolling bearing 50 of the present embodiment is a single row cylindrical roller bearing, and includes an outer ring 51 having an outer ring raceway surface 51a on an inner peripheral surface, an inner ring 52 having an inner ring raceway surface 52a on an outer peripheral surface, an outer ring raceway surface 51a and an inner ring. The roller 53 which is a some rolling element arrange | positioned so that rolling is possible between the track surfaces 52a, and the synthetic resin holder | retainer 54 of the single annular ring structure which hold | maintains the roller 53 of each row | line | column, respectively are provided.

  As shown in FIGS. 9B and 9C, the retainer 54 includes an annular portion 61 and a plurality of cantilever pillar portions 62 extending from one side surface 61a of the annular portion 61. The rollers 53 are accommodated in the respective pockets 63 formed by the annular part 61 and the column part 62 adjacent thereto. The circumferential side surface 62a of the pillar portion 62 constituting the inner surface of the pocket 63 has a cylindrical surface 64a having a radius of curvature R on the radially outer side than the PCD of the roller 33 and a cylindrical surface 64a on the radially inner side of the PCD. , And a flat surface 64b that is formed between the cylindrical surface 64a and the outer peripheral edge of the column part 62. Further, the column part 62 includes a protrusion 66 that is sandwiched between the pair of flat surfaces 64b and extends inward in the radial direction to prevent axial rolling.

  By adopting such a cage shape, the pillar portion 62 of the cage 54 is reduced in cross-sectional thickness from the annular portion 61 toward the tip portion, the weight of the cage 54 is reduced, and due to centrifugal force. Expansion of the column part 62 is relieved.

  Also in the present embodiment, a structure in which a predetermined amount of deformation due to a centrifugal force is inclined inward in the radial direction by an angle β from the annular portion 61 toward the tip portion of the column portion 62, and the centrifugal force during high-speed rotation is used. When the deformation occurs, the inclination is corrected, the column part 62 becomes substantially horizontal in the axial direction, and the contact position between the roller 53 and the pocket 63 of the cage 54 becomes appropriate. In this case, the boundary edge 65 between the cylindrical surface 64a of the column portion 62 and the outer diameter side flat surface 64c constitutes a guide portion that is inclined inward in the radial direction. It is regulated by this boundary edge 65.

In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.
The cage of the one-side annular ring structure of the present invention can be applied to other ball bearings such as an angular ball bearing in addition to the deep groove ball bearing described above, and the above-described single row cylindrical roller bearing and double row cylindrical roller bearing. In addition, the present invention can be applied to other roller bearings.

Moreover, although the intensity | strength of a ring part changes with the shape of a ring part, and centrifugal force expansion amount also changes, when the interference with a holder | retainer and a seal part is considered, the following values ( _TC1 , _TC2 ) are 10%- 40%, preferably 15% to 35% is desirable.

In the case of ball bearings,
T _C1 = Cage bottom thickness (L ₁ ) / ball diameter (Da ₁ ) × 100 (%)
For cylindrical roller bearings,
T _C2 = Cage bottom thickness (L ₂ ) / Roller diameter (Da ₂ ) × 100 (%)
As the ratio of the ball diameter to the inner / outer radial cross-sectional width or the axial cross-sectional width of the bearing is larger, it is desirable to select the smaller one of the above-mentioned regions for T _C1 and T _C2 . In addition, refer to FIG. 2 and FIG. 7 for the cage bottom thicknesses L ₁ and L ₂ , the ball diameter Da ₁ , and the roller diameter Da ₂ .

For example, in a cage having a single annular ring structure applied to a deep groove ball bearing as shown in FIG. 2, T _C1 and the inclination angle of the column part are designed as shown in Table 1.

  Furthermore, in the present invention, the predetermined centrifugal force that deforms the column part 22 so that the column part 22 is parallel to the axial direction has a dmn value of 800,000 or more, preferably 900,000 or more, more preferably 1,000,000. The above centrifugal force is intended.

It is sectional drawing of the deep groove ball bearing which concerns on 1st Embodiment of this invention. It is sectional drawing of the holder | retainer of the single annular ring structure of FIG. (A) is a top view of the retainer of the single annular ring structure of the first modification, and (b) is a top view of the retainer of the single annular ring structure of the second modification. (A) is sectional drawing of the holder | retainer of the single annular ring structure of a 3rd modification, (b) is the top view. (A) is sectional drawing of the holder | retainer of the single annular ring structure of a 4th modification, (b) is sectional drawing along the VV line. (A) is sectional drawing of the deep groove ball bearing which concerns on 2nd Embodiment, (b) is sectional drawing of the holder | retainer of the one annular ring structure. (A) is sectional drawing of the double row cylindrical roller bearing which concerns on 3rd Embodiment, (b) is sectional drawing of the holder | retainer of the single annular ring structure, (c) is VII of (b) It is the figure seen from the direction. (A) is sectional drawing of the double row cylindrical roller bearing which concerns on 4th Embodiment, (b) is sectional drawing of the holder | retainer of the single annular ring structure, (c) is VIII of (b) It is the figure seen from the direction. (A) is sectional drawing of the single row cylindrical roller bearing which concerns on 5th Embodiment, (b) is sectional drawing of the holder | retainer of the one annular ring structure, (c) is IX of (b). It is the figure seen from the direction. It is a perspective view of the conventional 2 sheet holder. (A) is a perspective view of the holder | retainer of the conventional one annular ring structure, (b) is the sectional drawing. (A) is sectional drawing of the holder | retainer of another conventional one-ring ring structure, (b) is the top view, (c) is sectional drawing along the XII-XII line of (a). (D) is sectional drawing along the XII'-XII 'line of (c). It is a principal part disassembled perspective view of the other conventional 2 sheet holder. It is sectional drawing which shows the state which the holder | retainer of the single annular ring structure shown in FIG. 12 deform | transformed.

Explanation of symbols

10,10a Deep groove ball bearing (rolling bearing)
11, 31, 51 Outer ring 12, 32, 52 Inner ring 13 Ball (rolling element)
14, 34, 34a, 54 Cage 21, 41, 61 Ring part 22, 42, 62 Pillar part 23, 43, 63 Pocket 24, 25, 26, 27 Convex part (guide part)
30, 30a Double row cylindrical roller bearing (rolling bearing)
33, 53 Roller (rolling element)
42b Outer peripheral edge part (guide part)
42c Inner peripheral edge (guide section)
45,65 border edge (guide part)
50 Single row cylindrical roller bearing (rolling bearing)

Claims (4)

An annular portion and a plurality of cantilever pillar portions extending from one side surface of the annular portion are provided, and the rolling element is rolled into each pocket formed by the annular portion and the adjacent pillar portion. A rolling bearing comprising a synthetic resin cage that is movably accommodated,
The column portion has a guide portion that is guided by contact with the rolling element,
The column portion and the guide portion are inclined inward in the radial direction from the annular portion toward the tip end portion of the column portion in order to correct inclination due to deformation of the column portion due to centrifugal force during bearing rotation. The rolling bearing is characterized in that the inclination angle corresponds to an angle at which the column portion is deformed radially outward by the centrifugal force . The rolling bearing according to claim 1 , wherein the rolling element is a ball. The rolling bearing according to claim 1 , wherein the rolling element is a cylindrical roller. The rolling bearing according to any one of claims 1 to 3, wherein the dmn value is used at 900,000 or more .

Images