JP2008002534A - Retainer for bearings - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a retainer for bearings with high rigidity and high strength capable of maintaining lubrication performance inside a bearing constantly for a long period. <P>SOLUTION: The retainer 11 for the roller bearing revolves together with each rolling element along the inside of the bearing while holding a plurality of rolling elements (a tapered roller) 5 freely rotatably, and is partitioned by a series of annular portions 2, 4 continuous along the inside of the bearing in a peripheral direction a plurality of pillars 6 arranged circumferentially at prescribed intervals after extending along the inside of the bearing from the circular ring and internal peripheral surfaces 2s, 4s of the circular ring portion and inner wall surfaces 6s of a plurality of pillars, and the retainer comprises a plurality of pockets 8 which hold freely rotatably a plurality of rolling elements one by one, and in the internal wall surface of the pillar, at least a contact portion 6a to contact each rolling element outside the virtual circle PCD which ties mutual centers of a plurality of rolling elements after constituting the window angle θ of 0°-90° and an elongation part 6b which is situated in roughly inner side from the contact portion and marks a smaller angle ϕ than the window angle are provided. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a highly rigid and high strength cage for a bearing capable of maintaining the lubrication performance inside the bearing constant over a long period of time.

  2. Description of the Related Art Conventionally, various types of bearings that rotatably support a rotating mechanism are applied to industrial machines such as railway vehicles, automobiles, steel facilities, and construction machines. As such a bearing, there are a ball bearing that is applied when supporting a relatively small load and a roller bearing that is applied when supporting a relatively large load, which corresponds to high-speed rotation under a high load in recent years. For this reason, roller bearings are often used.

  As an example of a roller bearing, the tapered roller bearing shown in FIGS. 1 (a) and 1 (b) is formed on opposing surfaces of an inner ring 1 and an outer ring 3, and inner and outer rings 1 and 3, which are arranged so as to be relatively rotatable. A plurality of rolling elements 5 rotatably incorporated between the raceway surfaces 1s and 3s, and a holder 11 having a plurality of pockets 8 for rotatably holding the plurality of rolling elements 5 one by one. It is configured. In this case, it is assumed that each rolling element 5 is a tapered roller 5 whose rolling surface 5m (the surface rolling between the raceway surfaces 1s and 3s) has a tapered shape, and holds the tapered roller. As the vessel 11, a cage retainer 11 is used.

  In such a configuration, an annular flange protrudes along the raceway surfaces 1s, 3s on at least one side of either one of the inner and outer rings 1, 3 and both raceway surfaces 1s, 3s. In the drawing, a configuration in which annular flanges 7 and 9 protrude on both sides of the raceway surface 1s of the inner ring 1 is illustrated. Further, the raceway surfaces 1s and 3s of the inner and outer rings 1 and 3 are inclined along the focusing direction of the rotation center 5z (FIGS. 1B and 4A) of each tapered roller 5, and corresponding to this. The annular flanges 7 and 9 projecting on both sides of the raceway surface 1s of the inner ring 1 have different diameters at the projecting ends 7e and 9e. That is, one of the flanges 9 (hereinafter referred to as the large diameter flange 9) serves as a relatively large-diameter protruding end 9e, and the other flange 7 (hereinafter referred to as the small diameter flange 7) corresponds to the one flange 9. The protruding end 7e has a relatively small diameter.

  Thus, when the plurality of tapered rollers 5 roll between the raceway surfaces 1s and 3s of the inner and outer rings 1, 3, each tapered roller 5 has circular side surfaces 5e formed on both sides of the rolling surface 5m. Guided along the raceway surfaces 1s and 3s of the inner and outer rings 1 and 3 while being held by the guide surfaces 7s and 9s (FIGS. 1 (a), 4 (a) and 4 (b)) of the flanges 7 and 9. The At this time, each tapered roller 5 is held one by one in the plurality of pockets 8 formed in the cage 11 and rotates around the rotation center 5z.

  Further, the cage retainer 11 includes two annular portions 2 and 4 that are continuous in the circumferential direction between the inner and outer rings 1 and 3 and are arranged opposite to each other at a predetermined interval at the same center. A plurality of column parts 6 extending between the ring parts 2 and 4 and arranged along the ring parts 2 and 4 at equal intervals in the circumferential direction, and inner circumferences of the two ring parts 2 and 4 A plurality of pockets 8 defined by the surfaces 2 s and 4 s and inner wall surfaces 6 s on both sides of the plurality of column portions 6 are provided. In this case, the two annular portions 2, 4 are designed to have different diameters along the inclination direction of the raceway surfaces 1s, 3s of the inner and outer rings 1, 3. That is, one annular portion (large diameter side annular portion) 4 is designed to have a relatively larger diameter than the other annular portion (small diameter side annular portion) 2. The whole forms, for example, a truncated cone shape as shown in FIG.

  In such a cage retainer 11, a plurality of tapered rollers 5 are rotatably held one by one in each pocket 8 of the retainer 11. That is, in each tapered roller 5, its rolling surface 5m is held by the inner wall surface 6s of two adjacent column parts 6, and the circular side surfaces 5e formed on both sides of the rolling surface 5m are two annular rings. The inner peripheral surfaces 2s and 4s of the portions 2 and 4 are held. During the rotation of the bearing, the cage retainer 11 revolves along the space between the inner and outer rings 1 and 3 together with the tapered rollers 5 while holding the tapered rollers 5 one by one in the plurality of pockets 8. To do.

  At this time, in order to keep the rotational performance of the tapered roller 5 held in the pocket 8 constant, conventionally, as shown in FIG. 5, for example, a cage in which the window angle θ of each pocket 8 is set to a constant angle has been conventionally used. Proposed. Here, the window angle θ is an angle formed between the inner wall surfaces 6s of the two column portions 6 that define each pocket 8, and from the inner diameter side to the outer diameter side (that is, the column portion 6 of the cage-shaped cage 11). A tapered shape is formed from the inner surface 6in to the outer surface 6out).

  More specifically, in the cage retainer 11, the inner wall surface 6 s of each column portion 6 has a center 11 h (FIGS. 1A, 1 B, 6 A) of the retainer 11 and a tapered roller 5. Of the first reference line 11x passing through the center of rotation 5z (FIGS. 1B and 4A), the tapered roller 5 is set to have a constant inclination angle (window angle) θ. The rolling contact surface 5m is linearly contacted at one place (one point) P1 (FIG. 5). Thereby, the taper roller 5 in each pocket 8 rotates in line with the inner wall surface 6s of the column portion 6 without falling off from the pocket 8 during rotation of the bearing.

  In this case, in order to reduce the frictional resistance between the tapered roller 5 and the retainer 11 (the inner wall surface 6s of the column portion 6) during rotation of the bearing, for example, Patent Document 1 discloses an outer diameter side of the retainer 11 ( In particular, a technique has been proposed in which various indentations are formed in the outer diameter surface 6out) of the column portion 6 and a lubricant is stored therein to maintain the lubricating performance inside the bearing constant over a long period of time.

  However, the cage 11 in which various depressions are formed has a configuration in which stress is easily concentrated in the vicinity of the depression, and as a result, the rigidity and strength of the cage 11 may be reduced. In addition, a high-rigidity and high-strength cage is required for a railway vehicle bearing that rotates at a high speed under a high load. However, the cage 11 having various depressions can satisfy such a requirement. Not. Therefore, it is conceivable to use a metal cage having relatively high rigidity and strength. However, in such a metal cage, metal powder that is worn as the bearing rotates may be mixed into the lubricant. There is a possibility that the lubrication performance inside the bearing cannot be maintained constant over a long period of time.

Further, when the cage 11 was taken out and inspected after the bearing was used for a certain period of time, it was confirmed that a relatively large amount of lubricant adhered to the inner diameter surface 6in of each column portion 6. In this case, for example, if the area of the inner diameter surface 6in of each column part 6 is increased, the amount of lubricant adhering to the inner diameter surface 6in can be dramatically increased. In FIG. 5, the area of the inner diameter surface 6in of the column portion 6 is the width dimension I from the second reference line 11y (FIG. 1 (b)) passing through the center 11h of the retainer 11 and the center 6z of the column portion 6. _It is defined as ₀ . Therefore, by increasing such width I _0, it is possible to efficiently lubricate the internal bearings, it can be maintained constant over the lubrication performance of the bearing in long-term. However, a cage capable of realizing such an effect is not known.
JP 2005-121097 A

  The present invention has been made to solve such a problem, and the object thereof is to provide a highly rigid and high strength bearing retainer capable of maintaining the lubricating performance inside the bearing constant over a long period of time. Is to provide. Moreover, since the cross-sectional area of each pillar part can be enlarged as another effect, the intensity | strength of the said pillar part can be improved.

  In order to achieve such an object, the present invention is a bearing retainer that revolves along the inside of the bearing together with the plurality of rolling elements while rotatably holding the plurality of rolling elements inside the bearing, At least one annular portion that is continuous in the circumferential direction along the inside of the bearing, and a plurality of column portions that extend from the annular portion along the inside of the bearing and are arranged at predetermined intervals in the circumferential direction along the annular portion And a plurality of pockets which are partitioned by the inner peripheral surface of the annular portion and the inner wall surfaces of the plurality of column portions and rotatably hold the plurality of rolling elements one by one on the inner wall surface of the column portion. Is at least a contact angle that forms a window angle of 0 ° or more and 90 ° or less and contacts the rolling elements outside the virtual circle that connects the centers of the plurality of rolling elements, and is positioned inward from the contact portion. And an extending portion extending at an angle smaller than the window angle. It is.

  In the present invention, the contact portion is set in a planar shape having a predetermined inclination angle with respect to a first reference line passing through the center of the cage and the center of the rolling element, and the extending portion is the center of the cage. And a second reference line that passes through the center of the column part and is set to a plane that forms a predetermined inclination angle. In this case, the contact portion is set in a planar shape having a predetermined inclination angle with respect to the first reference line passing through the center of the cage and the center of the rolling element, and the extending portion has a predetermined curvature with respect to the contact portion. You may set in the circular arc shape which carries out tangent connection by a radius. The bearing cage of the present invention is entirely formed of a resin material, and can be applied to a bearing that supports a rotating shaft provided in a railway vehicle.

  ADVANTAGE OF THE INVENTION According to this invention, the highly rigid and high intensity | strength cage for a bearing which can maintain the lubricating performance inside a bearing constant over a long period of time is realizable.

  Hereinafter, a bearing cage according to an embodiment of the present invention will be described with reference to the accompanying drawings. This embodiment is an improvement of the cage retainer 11 (FIG. 6 (a)) used for the roller bearings (FIGS. 1 (a), (b) and 4 (a)) described above. Since the structure of the bearing is the same as that shown in the figure, only the cage 11 of the improved part will be described below. Here, for example, a cage 11 applied to a bearing that supports a rotating shaft (an axle, various drive shafts, etc.) provided in a railway vehicle such as a Shinkansen is assumed.

  As shown in FIGS. 1C to 1E, in the bearing retainer according to the present embodiment, the inner wall surface 6s of each column portion 6 has at least a window angle 2θ of 0 ° or more and 90 ° or less. The center of the plurality of tapered rollers 5 (rotation center 5z: FIG. 1 (b), FIG. 4 (a)), a contact portion 6a that contacts each tapered roller 5 outside the virtual circle PCD that connects each other; An extending portion 6b is provided which is located on the inner side from the contact portion 6a and extends at an angle 2φ smaller than the window angle 2θ.

  More specifically, the contact portion 6a includes the center 11h (FIGS. 1A, 1B, 6A) of the retainer 11 and the center of the tapered roller 5 (rotation center 5z: FIG. 1B). 4 (a)) is set to a plane that forms a predetermined inclination angle (window angle) θ with respect to the first reference line 11x passing through FIG. The extending portion 6b is set in a planar shape that forms a predetermined inclination angle φ with respect to the second reference line 11y that passes through the center 11h of the cage 11 and the center 6z of the column portion 6.

In this case, the inclination angle (window angle) θ of the contact portion 6a and the inclination angle φ of the extending portion 6b are preferably set so as to satisfy the following expression (1).
180 / Z + θ> φ ≧ 0 (1)
Z indicates the total number of tapered rollers 5.

  As described above, according to the present embodiment, the inclination angles θ and φ of the two contact portions 6a and the extending portion 6b are set on the inner wall surface 6s of each column portion 6 so as to satisfy the above expression (1). Thus, the area of the inner diameter surface 6in of the column portion 6 can be significantly increased as compared with the conventional case. In this case, the extending portion 6b provided on the inner diameter surface 6in side of the column portion 6 extends from the connection boundary P3 with the contact portion 6a toward the tapered roller 5, and the extending end P2 has a rolling surface 5m. Is positioned in a non-contact state. For this reason, the inner wall surface 6s of the column portion 6 is configured to come into contact with the tapered roller 5 at one point (one point) P1 of the contact portion 6a.

In such a configuration, when defining the area of the inner diameter surface 6in column portions 6 as the width I from the second reference line 11y, the width I is greater than the conventional width I ₀ (I> I ₀ ). That is, by configuring the inner wall surface 6s (the contact portion 6a and the extending portion 6b) of the column portion 6 so as to satisfy the above formula (1) (FIG. 1 (e)), the configuration of the conventional column portion 6 ( Compared to FIG. 5), the area (width dimension I, cross-sectional area) of the inner diameter surface 6in of the column portion 6 of the present embodiment can be set larger (I> I ₀ ). In this case, the area (width dimension I) of the inner diameter surface 6in can be set larger than the conventional one by the number of (I−I ₀ ) × 2 × columns 6. Thereby, the amount of lubricant adhering to the inner diameter surface 6in can be dramatically increased. As a result, the inside of the bearing can be efficiently lubricated, and the lubricating performance inside the bearing can be maintained constant over a long period of time. Furthermore, the strength of the column 6 and further the strength of the cage 11 can be improved by the amount that the cross-sectional area of each column 6 can be increased.

  In addition, according to the present embodiment, there is no need to form various depressions for storing the lubricant on the outer diameter side of the retainer 11 (particularly, the outer diameter surface 6out of the column portion 6). A difficult cage configuration can be realized. Thereby, the rigidity and strength of the cage 11 can be set high. As a result, even when the cage 11 is applied to a railway vehicle bearing that rotates at high speed under a heavy load, the above-described lubrication performance is maintained, and the rotational stability and safety of the bearing are maintained over a long period of time. It becomes possible to do.

  In the embodiment described above, the values of the inclination angles θ and φ of the two contact portions 6a and the extending portions 6b are not particularly mentioned, but the inclination angle (window angle) θ is, for example, that of the tapered roller 5 Since it is arbitrarily set according to the size (diameter), the position of the retainer 11 between the inner and outer rings 1 and 3, the shape and type of the retainer 11, the numerical value is not particularly limited here. In addition, the inclination angle φ is arbitrarily set according to the number, size, shape, and the like of the column parts 6, and is not specifically limited here.

  In the above-described embodiment, the connection boundary P3 between the contact portion 6a and the extension portion 6b has an angular shape on the drawing. However, the fillet is provided here to round the corner. May be. Stress is relatively easily concentrated on the angular portion, but by providing a fillet, the contact portion 6a and the extending portion 6b can be smoothly continuous, and as a result, the strength of the cage 11 Can be improved.

  Further, even when a cage retainer 11 as shown in FIG. 2 is applied as a bearing retainer according to another embodiment of the present invention, the same as the above-described embodiment (FIG. 1 (e)). The effect can be realized. In the cage 11, the contact portion 6 a has a planar shape that forms a predetermined inclination angle (window angle) θ with respect to the first reference line 11 x that passes through the center 11 h of the cage 11 and the rotation center 5 z of the tapered roller 5. The extending portion 6b is set in an arc shape tangentially connected to the contact portion 6a with a predetermined radius of curvature R.

  According to such another embodiment, since the extending portion 6b is formed in an arc shape, the contact point P1 between the inner wall surface 6s (contact portion 6a) and the tapered roller 5 can be hardly changed during rotation of the bearing. It becomes possible to further improve the rotational stability of the bearing. Further, by connecting the arc-shaped extending portion 6b tangentially to the contact portion 6a with a predetermined radius of curvature R, it becomes possible to smoothly connect the contact portion 6a and the extending portion 6b. The strength of the cage 11 can be improved. Since other effects are the same as those of the above-described embodiment, description thereof is omitted.

  Moreover, in each embodiment mentioned above (FIG.1 (e), FIG.2), although it did not mention in particular about the surface shape of the inner wall surface 6s (the contact part 6a and the extension part 6b) of the pillar part 6, It is good also as a holder | retainer structure as shown to Fig.3 (a), (b). That is, in the region of the inner wall surface 6 s of each column portion 6 near the small-diameter-side annular portion 2, each of the tapered rollers 5 together with the retainer 11 is incorporated into the inside of the bearing (in the drawing, the inner ring 1). A contact portion that contacts the roller 5 is formed, and a non-contact portion 6c that is always in non-contact with each tapered roller 5 is formed in an area near the large-diameter-side annular portion 4 of the inner wall surface 6s of each column portion 6. Is formed. In this case, the two contact portions 6a and the extending portion 6b described above are provided in the region where the contact portion is formed in the inner wall surface 6s.

FIG. 3A shows a contact portion formed in a substantially trapezoidal shape along the inner wall surface 6s as the first cage configuration. Such a contact portion passes through both sides of the column portion 6 from the end portion 6e of the column portion 6 joined to the small-diameter side annular portion 2 and toward the end portion 6e of the large-diameter side annular portion 4 in the axial direction (the bearing). It has a tapered shape about the rotation center axis Q (in a direction parallel to FIG. 1A), and extends so as to enter the inner diameter side of the large-diameter side annular portion 4 as it is.
FIG. 3B shows a contact portion formed in a substantially rectangular shape along the inner wall surface 6s as the second cage configuration. Such a contact portion has a radial direction from the end portion 6e of the column portion 6 joined to the small-diameter-side annular portion 2 (direction perpendicular to the rotation center axis Q of the bearing (FIG. 1A)). It is formed across.

  According to the first and second cage configurations, as shown in FIG. 4B, when the plurality of tapered rollers 5 are assembled together with the cage 11 into the inner ring 1 from which the annular flange portion 7 is projected. Only the contact portions (contact portions 6a and extending portions 6b) of the column portions 6 are pressed by the tapered rollers 5 in contact with the protruding ends 7e of the flange portion 7, and the non-contact portions 6c of the inner wall surface 6s are Each tapered roller 5 does not contact. For this reason, only the small diameter side annular portion 2 is expanded in the outer diameter direction. In this state, by moving the inner ring 1 further in the direction of arrow Y, each tapered roller 5 held by the retainer 11 gets over the protruding end 7e of the flange 7 and is incorporated into the raceway surface 1s of the inner ring 1. Can do.

  As described above, when each tapered roller 5 is assembled to the raceway surface 1s of the inner ring 1, only the small-diameter-side annular portion 2 is expanded in the outer diameter direction, so that the entire cage is expanded. The tightening force (compression force) acting between each tapered roller 5 and the raceway surface 1s of the inner ring 1 can be reduced. As a result, it is possible to suppress the occurrence of problems such as damage or breakage of each tapered roller 5 or inner ring 1 (track surface 1s) during assembly.

  In addition, in the inner wall surface 6s of each column part 6, the contact part (the contact part 6a and the extension part 6b) protrudes in the direction which narrows the opening of the pocket 8 so that it may contact with the rolling surface 5m of the tapered roller 5. On the other hand, the non-contact portion 6c is formed by retracting the opening of the pocket 8 so as to be separated from the rolling surface 5m of the tapered roller 5. In this case, the amount of business trip of the contact portion ((contact portion 6a and extension portion 6b)) and the amount of retraction of the non-contact portion 6c are, for example, the shape and size of the cage 11, the shape and size of the pocket 8, or Since it is arbitrarily set according to the shape and size of the rolling surface 5m of the tapered roller 5 held in the pocket 8, there is no particular limitation here.

  Further, in the first and second cage configurations, the formation region (for example, length, width, etc.) of the contact portion ((contact portion 6a and extension portion 6b)) is, for example, the type and shape of the cage 11, Since it is arbitrarily set depending on the size and rigidity, it is not particularly limited here. For example, as the third cage configuration, as shown in FIG. 3C, the two contact portions 6 a described above are arranged over the entire inner wall surface 6 s of each column portion 6 and along the longitudinal direction of the column portion 6. And the extension part 6b may be provided.

  In each of the above-described embodiments (FIGS. 1 (e) and 2), the material of the cage retainer 11 is not particularly mentioned, but the whole may be formed of a resin material, or metal You may shape | mold with a material. In this case, any material can be selected as the material of the cage 11 as long as it has high rigidity and high strength, and is not particularly limited here. Further, since the bearing is exposed to high temperatures during rotation of the bearing, it is preferable to select a material having excellent heat resistance.

Moreover, in each embodiment mentioned above (FIG.1 (e), FIG.2), although the tapered roller was assumed as the rolling element 5, and it demonstrated supposing the holder | retainer 11 which can hold | maintain this, For example, the above-described effects can be realized by applying the technical configuration of the present invention to the cage 11 that can hold cylindrical rollers, needle rollers, spherical rollers, convex rollers, and the like.
Moreover, in each embodiment mentioned above, in the inner wall surface 6s of each pillar part 6, it contacts with the tapered roller 5 at one place (one point) P1 of the contact part 6a, and the extension end P2 of the extension part 6b. Exemplifies a configuration in which the tapered roller 5 is not in contact with each other. However, the configuration is not limited to this, and one (one point) P1 of the contact portion 6a and the extending end P2 of the extending portion 6b are both. It is good also as a structure which contacts with respect to the tapered roller 5. FIG.

  Further, as the cage 11 according to the modified example of the present invention, for example, as shown in FIG. 6A, at the four corners of each pocket 8, it is adjacent to both end portions 6e of the column portion 6 in the annular portions 2, 4. You may provide the escape part 10 formed in the part which was depressed by predetermined depth. In this case, the relief portions 10 are provided at the four corners of each pocket 8 and are formed to be recessed (recessed) in the direction along the rotation center axis Q of the bearing (FIG. 1A). In other words, each relief portion 10 is not formed to be recessed (recessed) along the bearing rotation direction.

  More specifically, as shown in FIGS. 6B to 6D, the relief portion 10 includes a flat surface 10s formed flat across the annular portions 2, 4 and a flat surface. It is composed of two arcuate surfaces R1 and R2 that are continuous with a predetermined curvature (for example, a radius of curvature) from both sides of the surface 10s toward the annular portions 2 and 4 and the column portion 6. Here, the flat surface 10s is formed so as to cross the annular portions 2 and 4 in parallel along the direction orthogonal to the rotation center axis of the bearing, and one of the two arc-shaped surfaces R1 and R2. The arcuate surface R1 is continuous from one side of the flat surface 10s to the inner peripheral surfaces 2s and 4s of the annular portions 2 and 4, and the other arcuate surface R2 is from the other side of the flat surface 10s. It is continuous with the inner wall surface 6 s of the column portion 6.

  In such a relief portion 10, assuming that the overall width dimension from the two arcuate surfaces R1, R2 to one flat surface 10s is 2n, the width dimension 2n is the end face of the tapered roller 5 (the rolling surface 5m and It is set to be larger than the dimensions (FIGS. 1A, 4A, and 4B) of a chamfer 5r formed on an annular end surface that is continuous with the side surface 5e along the circumferential direction. Further, the relief portion 10 is configured by setting the depth dimension k within a range of 10% to 30% of the width dimension H of the annular portions 2 and 4. Here, assuming that the depth dimension k of the relief portion 10 approximates the curvature radius ρ of the arcuate surfaces R1 and R2 (ρ = k), the ratio (ρ / H) of the curvature radius ρ and the width dimension H In terms of representation, the clearance 10 is set so as to satisfy the relationship of 0.1 ≦ ρ / H ≦ 0.3.

  In the drawing, each of the arcuate surfaces R1 and R2 is formed with a continuous constant (single) radius of curvature ρ. In this case, the magnitude of the radius of curvature ρ is, for example, the depth of the relief portion 10. Since it is arbitrarily set according to the length dimension k and the width dimension 2n, the numerical value is not particularly limited here. Further, the depth dimension k and the width dimension 2n of the relief portion 10 are arbitrary depending on, for example, the size and shape of a rolling element (cone roller) (not shown) and the size and shape of the pocket 8 that holds the rolling element (cone roller). Therefore, the numerical value is not particularly limited here.

  As described above, according to the cage 11 of this modification, the cage 11 is composed of two arcuate surfaces that are continuous with a predetermined radius of curvature ρ from both sides of one flat surface 10s toward the annular portions 2 and 4 and the column portion 6. By providing the relief portions 10 at the four corners of the pocket 8, excessive stress concentration at the four corners of the pocket 8 can be reduced even under a condition in which an increase in the radius of curvature is restricted. As a result, the strength of the cage 11 can be kept constant as compared with the conventional case. As a result, the life of the cage 11 can be extended and the reliability can be improved.

  Further, according to this modification, the width dimension 2n of the relief portion 10 is set larger than the dimension of the chamfer 5r of the tapered roller 5, thereby preventing scraping of the lubricant (grease, oil) enclosed in the bearing. Further, uneven wear of the pocket 8 of the cage 11 can be prevented. That is, at the four corners of each pocket 8, it becomes possible to adhere and hold the lubricant to the end face of the tapered roller 5, whereby the annular flange 7 formed on the end face of the tapered roller 5 and the inner and outer rings 1, 3. , 9 (the roller guide projecting on both sides of the raceway surface 1s) can be continuously supplied with the lubricant. As a result, it is possible to reduce wear and wear of the tapered roller 5 and the inner and outer rings 1 and 3, and to extend the life of the bearing.

  Furthermore, according to this modification, the depth k of the relief portion 10 is set in the range of 10% to 30% of the width dimension H of the annular portions 2 and 4, thereby increasing the strength of the cage 11 as a whole. It becomes possible to keep constant, and as a result, the rotational performance of the bearing can be kept constant over a long period of time. In particular, the bearings that support the rotating shafts (for example, axles) provided on high-speed railway vehicles such as the Shinkansen and the output shafts of the main motors are subjected to high loads under high-speed rotation. Although the container 11 is required to have a high strength, the retainer 11 of the present modification can sufficiently cope with this.

Here, the effect of the cage 11 of the present modification as described above will be demonstrated using a stress generation model.
FIG. 7 (a) shows a cage model in which the pocket 8 (FIG. 6) does not have the relief portion 10, and the annular portions 2, 4 have a thickness dimension T = 8 and a width dimension H = 10. The column portion 6 is set to have a length dimension E = 15 and a column length L = 20 to the center of the annular portion. Then, a load F = 50 (for example, 50 Newton) is applied to the column portion 6 to generate a moment M in the cage model. At this time, it is assumed that a uniform distributed load W acts on the column portion 6.

From the material mechanical relationship under such conditions, the stress σ ₀ (reference stress) generated in the column portion 6 is calculated as the following equation (1) from the following equations (2) and (3).
σ ₀ = M / Z (Z: section modulus) (1)
^{M = W · L 2/2} ... (2)
^{Z = T · H 2/6} ... (3)

FIG. 7 (b) shows a cage model having an existing relief portion 10a in the pocket 8 (FIG. 6). The relief portion 10a is formed at a portion adjacent to the end portion 6e of the column portion 6 at a single position. It has an arc shape formed with only one curvature radius ρ. In this case, when the bending stress generated in the annular portions 2 and 4 is obtained from the material mechanical relationship, the tensile stress σmax generated at the four corners of each pocket 8 in consideration of the stress concentration is calculated as Equation (4). The
σmax = ασ ₀ (α: Stress concentration factor) (4)

Here, structural analysis (FEM analysis) based on the finite element method is performed on the cage model of FIG. 7B, and from the σmax obtained from the analysis result and the reference stress σ ₀ obtained from the material mechanics. The stress concentration coefficient α is calculated as equation (5).
α = σmax / σ ₀ (5)

  FIG. 8 (a) shows the calculation result of the stress concentration coefficient α in the cage model of FIG. 7 (b). The radius of curvature of the relief portion 10a is ρ, the depth dimension is k, the annular portion 2 is shown. , 4 is H and ρ = k, the stress concentration coefficient α is an extreme value (α = 3.65 to 3.76, αmin = in the range of ρ / H = 0.1 to 0.3). It is understood that 3.39) is taken.

  FIG. 7 (c) shows a cage model of the present modified example having the existing relief portion 10 in the pocket 8 (FIG. 6), where the width dimension of the relief portion 10 is 2n, ρ / H = 0. When the stress concentration coefficient α is calculated based on this, a calculation result as shown in FIG. 8B is obtained. According to this calculation result, n / ρ = 1.0 is the dimensions (single curvature radius ρ) indicating the minimum value (αmin = 3.39) of the stress concentration coefficient α in FIG. It can be seen that when n / ρ exceeds 1.0, the stress concentration coefficient α decreases, and the effect of reducing stress concentration is exhibited. In this case, since n / ρ = 2.0 or later takes a substantially constant extreme value, it is preferable to set the relief portion 10 so that n / ρ is 2.0 or more.

(a) is a longitudinal sectional view of a tapered roller bearing, (b) is a transverse sectional view of FIG. (a), and (c) is a column portion in a bearing cage according to an embodiment of the present invention. Sectional drawing which expands and shows partially the structure of the inner wall surface formed in the outer-diameter surface side, (d) is a bearing retainer which concerns on one embodiment of this invention. Sectional drawing which expands and shows partially the structure of the formed inner wall surface, (e) is a figure which expands and shows the structure of the two contact parts and extension part which were formed in the inner wall surface of a pillar part. In the bearing retainer which concerns on other embodiment of this invention, the figure which expands and shows the structure of the two contact parts and extension part which were formed in the inner wall face of a pillar part. (a) is a cross-sectional view showing a partially enlarged view of the first cage structure of the present invention, (b) is a cross-sectional view showing a partially expanded view of the second cage structure of the present invention, (c) ) Is a partially enlarged cross-sectional view of the third cage structure of the present invention. (a) is sectional drawing which expands and shows a part of bearing in which the cage for bearings which concerns on one embodiment of this invention was integrated with the several rolling element, (b) is each rolling element to a bearing. The figure which shows the state incorporating. The figure which expands and shows a part of structure of the inner wall face of a pillar part in the conventional cage for bearings. (a) is a perspective view showing an overall configuration example of a bearing retainer according to a modification of the present invention, (b) is an enlarged view of a part of the retainer of FIG. (c) is the enlarged view which looked at some cages of the figure (a) from the inside, (d) is the figure which expands and shows the structure of an escape part. It is a figure which shows the generation | occurrence | production model of stress, (a) is a cage model without a relief part in a pocket, (b) is a cage model which has an existing relief part, (c) is this modification example. Cage model. It is a figure which shows the FEM analysis result of a stress concentration count, Comprising: (a) is the analysis result in the existing cage, (b) is the analysis result of the cage of this modification.

Explanation of symbols

2,4 torus
2s, 4s Inner peripheral surface 5 Rolling elements (cone rollers)
6 pillar part 6a contact part 6b extension part 6s inner wall surface 8 pocket 11 cage

Claims (8)

A bearing retainer that revolves along the inside of the bearing together with the plurality of rolling elements while holding the plurality of rolling elements within the bearing rotatably,
At least one annular portion that is circumferentially continuous along the bearing interior;
A plurality of pillars extending from the annular part along the inside of the bearing, and arranged at predetermined intervals in the circumferential direction along the annular part;
A plurality of pockets that are partitioned by an annular part and inner wall surfaces of a plurality of pillars, and that hold a plurality of rolling elements one by one,
A contact portion that contacts each rolling element at least outside a virtual circle that forms a window angle of 0 ° or more and 90 ° or less and connects the centers of the plurality of rolling elements on the inner wall surface of the column part, and a contact A bearing retainer is provided, wherein the bearing retainer is provided with an extending portion that is located inward from the portion and extends at an angle smaller than the window angle.   The contact portion is set in a planar shape having a predetermined inclination angle with respect to the first reference line passing through the center of the cage and the center of the rolling element, and the extending portion is formed between the center of the cage and the column portion. The bearing retainer according to claim 1, wherein the bearing retainer is set in a planar shape having a predetermined inclination angle with respect to a second reference line passing through the center.   The contact portion is set in a planar shape having a predetermined inclination angle with respect to the first reference line passing through the center of the cage and the center of the rolling element, and the extending portion is a predetermined shape with respect to the contact portion. 2. The bearing retainer according to claim 1, wherein the bearing retainer is set in an arc shape tangentially connected with a radius of curvature.   The bearing retainer according to claim 1, wherein the bearing retainer is entirely formed of a resin material. Each pocket is provided with a relief portion formed by recessing a portion of the annular portion adjacent to the pillar portion by a predetermined depth,
The escape portion includes one flat surface formed flat across the annular portion, and two arc-shaped surfaces continuous at a predetermined curvature from both sides of the flat surface toward the annular portion and the column portion. The bearing retainer according to any one of claims 1 to 4, wherein:   In a bearing in which a roller is applied as a rolling element, the relief portion is configured by setting the overall width dimension from two arcuate surfaces to one flat surface larger than the chamfer dimension formed on the end surface of the roller. The bearing retainer according to claim 5, wherein the bearing retainer is provided.   The bearing retainer according to claim 5 or 6, wherein the relief portion is configured with a depth dimension set in a range of 10% to 30% of a width dimension of the annular portion. The bearing retainer according to any one of claims 1 to 7, wherein the bearing retainer is applicable to a bearing that supports a rotating shaft provided in a railway vehicle.

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