CN108457986B - Cylindrical roller bearing and retainer thereof - Google Patents
Cylindrical roller bearing and retainer thereof Download PDFInfo
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- CN108457986B CN108457986B CN201710094023.7A CN201710094023A CN108457986B CN 108457986 B CN108457986 B CN 108457986B CN 201710094023 A CN201710094023 A CN 201710094023A CN 108457986 B CN108457986 B CN 108457986B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/38—Ball cages
- F16C33/3887—Details of individual pockets, e.g. shape or ball retaining means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
The invention relates to a cylindrical roller bearing and a retainer thereof. The roller of the cylindrical roller bearing of the invention is a stepped shaft-shaped roller with thick middle and thin two ends, the pocket hole is a frame-shaped structure which is matched with the shape of the stepped shaft-shaped roller and thick middle and thin two ends, when the bearing rotates, the peripheral surfaces of the small diameter sections at the two ends of the stepped shaft-shaped roller are in sliding fit with the section side walls at the two ends of the pocket hole, so that the stepped roller exerts driving force for driving the retainer to rotate on the retainer through the pocket hole section side walls when rotating around the inner ring, the thick middle part is respectively contacted with the inner ring and the outer ring of the bearing and a gap is reserved between the thick middle part and the pocket hole, when the bearing rotates, the roller drives the retainer to rotate through the small diameter sections at the two ends, and the thick cylindrical part in the middle of the roller is only contacted and matched with the inner ring and the outer ring of the bearing, thus the friction force between the roller and the retainer is completely transferred to the small diameter sections at the two ends, the service life of the bearing is prolonged.
Description
Technical Field
The invention relates to a cylindrical roller bearing and a retainer thereof.
Background
The bearings of the aviation turbojet engine mostly adopt cylindrical roller bearings, and the bearings usually work at high speed (the DN value reaches 3 multiplied by 10 at present)6mm.r/min) and under high temperature and light load.
The Chinese patent with the bulletin number of CN 101910660B and the bulletin date of 2013.03.13 discloses a cylindrical roller bearing, wherein a plurality of pockets for mounting cylindrical rollers are uniformly distributed in the circumferential direction of an annular body of a retainer of the bearing, the cylindrical rollers are mounted in the pockets and are in contact with an inner ring and an outer ring of the bearing, the circumferential limiting is carried out on the cylindrical rollers by the front side wall and the rear side wall of the pockets, and the cylindrical rollers rotate between the inner ring and the outer ring of the bearing in the rotating process and drive the retainer to rotate through the side wall of the pockets. The matching surfaces of the rollers of the bearing, which are in rolling fit with the inner ring and the outer ring, not only bear the friction force of the inner ring and the outer ring, but also can bear the friction force generated by the pocket holes on the retainer when the retainer is driven to rotate.
Disclosure of Invention
The invention aims to provide a cylindrical roller bearing with the matching surfaces of a roller and an inner ring and an outer ring not easy to wear; meanwhile, the invention also provides the retainer of the cylindrical roller bearing.
In order to achieve the purpose, the cylindrical roller bearing retainer adopts the following technical scheme: cylindrical roller bearing holder, including the axis along the annular body that extends in the left and right directions and radially link up the pocket hole of setting on annular body, the lateral wall of pocket hole is narrow, the wide frame shape in the middle of both ends in the projection shape of radial direction, and the narrow part in pocket hole both ends has two circumference relative, is used for with the terminal side wall of the outer peripheral face sliding fit of the thin step shaft shape roller in middle thick both ends's both ends path section, and the wide part in the middle of the pocket hole has two circumference relative, is used for with the middle outer peripheral face clearance fit's of the thin step shaft shape roller in middle thick both ends middle side wall.
The width of both end portions of the pocket is the same.
The back lateral wall in the end lateral wall of pocket is in the positive slope of the direction of rotation of the cyclic annular body of outside from inside in radial direction.
The tangent value of the inclination angle of the rear side wall of the end side walls of the pocket is equal to or greater than the friction coefficient between the outer peripheral surface of the roller and the rear side wall of the pocket.
The preceding lateral wall in the end lateral wall of pocket is in the positive slope of the direction of rotation of the cyclic annular body of outside from inside in the radial direction.
The tangent value of the inclination angle of the front wall of the end side walls of the pocket is equal to the coefficient of friction between the outer circumferential surface of the roller and the front wall of the pocket.
The cylindrical roller bearing adopts the following technical scheme: cylindrical roller bearing, including inner circle, outer lane and holder, the holder includes the axis along the annular body that extends in the left and right directions and sets up the pocket hole on annular body, is equipped with the roller in the pocket hole, the roller is the thin step shaft shape roller in the thick both ends in the middle, the lateral wall of pocket hole in radial direction on the projection shape be with the shape adaptation of roller, the narrow wide frame shape in the middle of the both ends is narrow, the narrow part in pocket hole both ends have two circumference relative, be used for with the outer peripheral face sliding fit's of the thin step shaft shape roller in the thick both ends lateral wall in both ends section in the middle of, the wide part in the middle of the pocket hole have two circumference relative, be used for with the thick both ends thin step shaft shape roller in the middle of the outer peripheral face clearance fit's of the middle major diameter section in the middle of lateral.
The diameters of the thinner end portions of the stepped shaft-shaped rollers are the same.
The back lateral wall in the end lateral wall of pocket is in the positive slope of the direction of rotation of the cyclic annular body of outside from inside in radial direction.
The tangent value of the inclination angle of the rear side wall of the end side walls of the pocket is equal to or greater than the friction coefficient between the outer peripheral surface of the roller and the rear side wall of the pocket.
The preceding lateral wall in the end lateral wall of pocket is in the positive slope of the direction of rotation of the cyclic annular body of outside from inside in the radial direction.
The tangent value of the inclination angle of the front wall of the end side walls of the pocket is equal to the coefficient of friction between the outer circumferential surface of the roller and the front wall of the pocket.
The invention has the beneficial effects that: the roller of the cylindrical roller bearing is a stepped shaft-shaped roller with thick middle and thin two ends, the pocket hole on the retainer is of a frame-shaped structure which is matched with the shape of the stepped shaft-shaped roller and thick middle and thin two ends, when the bearing rotates, the outer peripheral surfaces of the small-diameter sections at the two ends of the stepped shaft-shaped roller are in sliding fit with the end side walls at the two ends of the pocket hole, so that the stepped roller exerts driving force for driving the retainer to rotate on the retainer through the side walls at the ends of the pocket hole when rotating around an inner ring, the thick middle part is respectively contacted with the inner ring and the outer ring of the bearing, gaps are reserved between the thick middle part and the pocket hole, when the bearing rotates, the roller drives the retainer to rotate through the small-diameter sections at the two ends, and the thick cylindrical part in the middle of the roller is only contacted and matched with the inner ring and the outer ring of the bearing, so that the friction force between the roller, The matching surface between the outer rings is excessively worn, so that the service life of the bearing is prolonged;
furthermore, the diameters of the cylindrical parts at the two thinner ends of the stepped shaft-shaped roller are the same, so that the stepped shaft-shaped roller is convenient to process;
furthermore, the rear side walls at the two ends of the pocket are inclined in the radial direction from inside to outside towards the positive direction of the rotation direction of the annular body, the rollers drive the retainer to rotate through the pocket in the rotation process, the contact force between each roller and the inner ring is reduced under the action of centrifugal force and vibration impact to generate slipping, the slipping rollers can continue to revolve around the inner ring under the drive of the rear side walls of the pocket, at the moment, the rollers are subjected to the positive pressure of the rear side walls on the rollers and the friction force between the outer peripheral surfaces of the rollers and the rear side walls, wherein the positive pressure faces the rotation direction of the retainer, the direction of the positive pressure is perpendicular to the rear side walls, the friction force faces the radial outer side of the bearing along the rear side walls, and the inclination of the rear side walls enables the direction of the resultant force of the positive pressure and the friction force to rotate for a certain angle towards the, at the moment, the radial outward force applied to the roller is correspondingly reduced, so that the radial inward force applied to the roller is increased, and finally, the contact force between the roller and the inner ring is increased, thereby being beneficial to restraining the slipping trend of the roller, reducing the abrasion caused by the slipping of the roller and prolonging the service life of the cylindrical roller bearing;
furthermore, the tangent value of the inclination angle of the rear side wall is greater than the friction coefficient between the outer peripheral surface of the roller and the rear side wall of the pocket, so that the resultant force of the positive pressure of the rear side wall on the slipping roller and the friction force rotates towards the inner side of the bearing and finally towards the radial inner side of the bearing, the resultant force generates a radially inward component force, and the contact force between the roller and the inner ring is further increased;
furthermore, the front side wall of the pocket is inclined in the radial direction from inside to outside towards the positive direction of the rotation direction of the annular body, the retainer is driven to rotate by the non-slip roller through the front side wall of the pocket during the rotation process, the front side wall of the pocket is subjected to the positive pressure of the non-slip roller and the friction force between the outer circumferential surface of the non-slip roller and the front side wall of the pocket, the resultant force of the positive pressure and the friction force finally acts on the front side wall of the pocket to enable the retainer to rotate, and the resultant force of the positive pressure and the friction force rotates for a certain angle towards the inner side of the bearing due to the positive inclination of the front side wall of the pocket from inside to outside towards the rotation direction of the annular body in the radial direction, so that the component force of the resultant force of the positive pressure and the friction force in the radial direction is reduced, and the component force for driving the retainer to rotate is, the radial outward component force borne by the retainer is reduced, so that the disturbance borne by the retainer in the radial outward direction is weakened, and finally the retainer is stably rotated under the driving of the non-slip roller, so that the stability of the bearing is improved;
furthermore, the tangent value of the inclination angle of the front side wall is equal to the friction coefficient between the outer peripheral surface of the roller and the front side wall of the pocket, so that the resultant force of the positive pressure and the friction of the roller on the front side wall of the pocket is consistent with the tangential direction of the bearing raceway and faces forwards along the bearing raceway, and the retainer is driven to rotate by the resultant force of the positive pressure and the friction at the maximum efficiency.
Drawings
FIG. 1 is a schematic structural view of an embodiment of a cylindrical roller bearing of the present invention;
FIG. 2 is a schematic structural view of the cage of FIG. 1;
FIG. 3 is a schematic cross-sectional view of FIG. 2;
FIG. 4 is a schematic view of the roller of FIG. 1;
FIG. 5 is a schematic view of the outer race of FIG. 1;
FIG. 6 is a schematic view of the small diameter section of a non-slipping roller exerting a force component on the front sidewall at one end of the pocket;
FIG. 7 is a schematic view of a force analysis of a rear sidewall at one end of a pocket on a small diameter section of a slipping roller;
in the drawings: 1. an outer ring; 2. a holder; 3. an inner ring; 4. a roller; 11. a raceway; 21. a pocket hole; 41. a large diameter section; 42. a small diameter section; 43. an end face; 211. a front side wall; 212. a rear sidewall; 213. a middle sidewall; 214. erecting a wall; n, positive pressure of the non-slip roller on the front side wall of the pocket; t, friction force of the non-slip roller to the front side wall of the pocket; F. the resultant force of the positive pressure N of the non-slip roller to the front side wall of the pocket and the frictional force T of the non-slip roller to the front side wall of the pocket; n1, positive pressure of the rear side wall of the pocket on the slipping roller; t1, friction of the rear side wall of the pocket against the slipping roller; f1, the resultant force of the positive pressure N1 of the rear side wall of the pocket against the slipping roller and the frictional force T1 of the rear side wall of the pocket against the slipping roller; theta, the inclination angle of the front side wall of the pocket; a. the angle of inclination of the rear sidewall of the pocket; b. the angle between the positive pressure N1 of the rear wall of the pocket against the slipping roller and the frictional force F1 of the rear wall of the pocket against the slipping roller.
Detailed Description
The following further describes embodiments of the present invention with reference to the drawings.
As shown in fig. 1 to 7, for convenience of description, in the embodiment of the present invention, the rotation direction of the cage is a forward direction, the side wall of the pocket on the front side in the rotation direction of the cage is a front side wall, and the side wall on the rear side is a rear side wall. The cylindrical roller bearing comprises an inner ring 3, an outer ring 1 and a retainer 2, wherein the retainer comprises an annular body extending left and right in the axial direction, a pocket 21 arranged on the annular body, and a roller 4 arranged in the pocket 21.
As shown in fig. 4, the roller 4 is a stepped shaft-shaped roller with a thick middle and thin two ends, and includes a large diameter section 41 in the middle and small diameter sections 42 coaxially disposed at two ends of the large diameter section 41, and the two small diameter sections 42 have the same diameter, so as to facilitate processing. The pockets 21 on the cage 2 are in a frame-shaped structure which is matched with the shape of the roller 4 and has a thick middle part and two thin ends, the middle part of the frame-shaped structure is provided with two opposite middle side walls 213, the width between the two middle side walls 213 and the length in the left-right direction are matched with the length of the large-diameter section 41 of the roller 4, the two ends of the frame-shaped structure are provided with two circumferentially opposite end side walls, the section side walls comprise a front side wall 211 and a rear side wall 212, and the width between the front side wall 211 and the rear side wall 212 and the length in the left-right direction are matched with the small-diameter sections 42 at the two ends of the roller 4. Specifically, the fit clearance between the two opposite middle side walls 213 of the pocket and the large-diameter section 41 of the roller 4 is larger than the fit clearance between the front side wall 211 and the rear side wall 212 of the pocket and the small-diameter section 42 of the roller 4, so that when the roller 4 drives the cage 2 to rotate, only the small-diameter sections 42 at the two ends are in contact with the cage 2, and the large-diameter section 41 of the roller 4 is only in contact with the inner ring and the outer ring of the bearing, thereby avoiding the abrasion of the roller caused by the friction between the cage and the large-diameter section 41 of the roller 4. Meanwhile, the small-diameter sections 42 at the two ends of the roller 4 are thinner in diameter, and the rotating speed of the roller is unchanged, so that the linear speed of the periphery of the small-diameter sections 42 at the two ends of the roller 4 is reduced, the friction loss and the friction temperature rise at the position are reduced, and the wear degree of the bearing is further reduced. A certain lubrication gap is reserved between the end surface 43 of the small-diameter section 42 at the two ends of the roller 4 and the upright wall 214 which is arranged oppositely at the left and right of the two ends of the pocket, a certain gap is reserved between the excessive step surface between the large-diameter section 41 and the small-diameter section 42 of the roller 4 and the pocket, and the gap is larger than the lubrication gap between the end surface 43 and the upright wall 214, so that the large-diameter section 42 of the roller 4 is not contacted with the retainer completely in the rotating process, and the abrasion of the roller caused by the friction between the large-diameter section 42 of the roller 4 and the retainer is avoided.
As shown in fig. 3, the rotation direction of the cage is as indicated by the arrow in the figure, the shape of the pocket 21 is adapted to the shape of the roller 4, and the front side wall 211 and the rear side wall 212 of the small width portion at both ends of the pocket 21 are each inclined in the radial direction from the inside to the outside toward the positive direction of the rotation direction of the cage, wherein the inclination angle of the front side wall is θ and the inclination angle of the rear side wall is a. The distance between the front and rear side walls of the pocket 21 is slightly larger than the diameter of the roller, so that a certain lubrication gap is left between the front and rear side walls and the cylindrical surface of the roller, which is beneficial for the entry of lubricating oil and lubricates the contact position of the roller and the retainer.
The cylindrical roller bearing in this embodiment is an outer guide type bearing, as shown in fig. 5, a raceway 11 of a roller is provided on an inner periphery of an outer ring 1, the raceway 11 is provided on the inner periphery of the outer ring 1, a cross section of the raceway 11 is a step shape adapted to a shape of the roller 4, and a total width of the raceway 11 is slightly larger than a length of the roller 4, so that a small lubrication gap is left between an end surface of the roller 4 and a groove wall of a ring groove, which is beneficial for lubricating oil to enter for lubrication.
After the cylindrical roller bearing is assembled in place, the roller is positioned between the inner ring and the outer ring, the cylindrical surface of the roller is respectively contacted with the outer circumferential surface of the inner ring and the inner circumferential surface of the raceway of the outer ring, and after the roller is assembled in place, a certain pre-tightening amount is required to be generated between the roller and the inner ring and between the roller and the outer ring so as to ensure that a certain contact force is generated between the cylindrical surface of the roller and the inner ring and. Fig. 6 and 7 show the force analysis schematic diagram between the roller and the front and rear side walls of the pocket during the rotation of the bearing, and the rotation directions of the inner ring and the roller are shown by arrows in the figure. Specifically, as shown in fig. 6, the rotation of the inner ring 3 drives the rollers 4 to self-transfer and revolve around the axis of the bearing in the raceway of the outer ring 1, the rollers 4 are in a non-slipping state at this time, the outer peripheral surface of the small diameter section 42 contacts with the front sidewall 211 of the pocket 21 and drives the cage 2 to rotate around the axis of the bearing during the revolution of the rollers 4, at this time, the cage receives a positive pressure N of the non-slipping rollers on the front sidewall 211 and a frictional force T between the outer peripheral surface of the non-slipping rollers and the front sidewall of the pocket, a resultant force F of the positive pressure N and the frictional force finally acts on the front sidewall of the pocket to rotate the cage, and since the front sidewall 211 of the pocket is inclined in the radial direction from the inside to the outside in the rotational direction of the ring body, a resultant force F of the positive pressure and the frictional force rotates by a certain angle toward the inside of the bearing, so that a component force F of the resultant, and the component force for driving the retainer to rotate is correspondingly increased, so that the non-slip roller is favorable for driving the retainer to rotate, the radial outward component force applied to the retainer is reduced, the disturbance applied to the retainer in the radial outward direction is weakened, and finally the retainer is stably driven by the non-slip roller to rotate, so that the stability of the bearing is improved. Meanwhile, because the tangent value of the inclination angle theta of the front side wall of the pocket is equal to the friction coefficient u between the outer peripheral surface of the roller and the front side wall of the pocket, namely tan theta = u, and u = T/N, the resultant force F of the positive pressure and the friction force is consistent with the tangential direction of the bearing raceway and is forward along the rolling direction, and the resultant force of the positive pressure and the friction force drives the retainer to rotate with the maximum efficiency. And the collision between the non-slip roller and the front side wall 211 is changed into oblique collision, so that collision impact is reduced, and the stability of the bearing is improved.
As shown in fig. 7, at this time, the roller 4 receives a larger centrifugal force, so that the contact force between the large diameter section 41 of the roller 4 and the inner ring 3 becomes smaller, at this time, although the roller 4 still contacts with the inner ring 3, the contact force between the two is not able to generate enough friction force to make the inner ring drive the roller to rotate, i.e. a relative slip phenomenon occurs between the roller and the inner ring, the movement of the roller generates a hysteresis phenomenon, due to the existence of a lubrication gap, the small diameter section 42 of the roller contacts with the rear sidewall 212 of the pocket, the cage drives the roller to continue to revolve through the rear sidewall 212, at this time, the roller receives a positive pressure N1 of the rear sidewall on the roller and a friction force T1 between the outer circumferential surface of the roller and the rear sidewall, wherein the positive pressure N1 faces the rotational direction of the cage and is perpendicular to the rear sidewall 212, the friction force T1 faces the, the rear side wall 212 is inclined, so that the direction of the resultant force F1 of the positive pressure and the friction force rotates towards the inner side of the bearing for a certain angle, the component force of the resultant force of the positive pressure and the friction force in the radial direction is reduced, the radial outward force applied to the roller is correspondingly reduced at the moment, the radial inward force applied to the roller is increased, and finally the contact force between the roller and the inner ring is increased, thereby being beneficial to restraining the slipping trend of the roller, reducing the abrasion caused by the slipping of the roller and prolonging the service life of the cylindrical roller bearing. Meanwhile, the tangent value of the inclination angle a of the rear side wall 212 is larger than the friction coefficient u between the rear side wall of the pocket and the outer peripheral surface of the roller, and u = N1/F1= tan b, then tan a > tan b, that is, the included angle b between the positive pressure N1 of the rear side wall of the pocket on the slipping roller and the friction F1 of the rear side wall of the pocket on the slipping roller is smaller than the inclination angle a of the rear side wall, so that the resultant force F1 of the positive pressure N1 and the friction T1 of the rear side wall 212 on the slipping roller rotates towards the inner side of the bearing and finally faces towards the radial inner side of the bearing, and the resultant force F1 generates a radially inward component force to further increase the contact force between the roller and the inner ring, and further suppress the slipping phenomenon of the roller. The collision between the rear side wall 212 and the roller is also changed into oblique collision, so that the collision impact between the cage and the roller is relieved, and the stability of movement is improved.
The cylindrical roller bearing has good anti-slip effect, can be used as a front bearing of a high-pressure worm gear of an aircraft engine or a middle bearing behind a high-pressure rotor and a low-pressure rotor, and can be applied to other occasions of unidirectional high-speed rotation.
In the above embodiment of the present invention, the front wall of the pocket satisfies a tangent value equal to a coefficient of friction between the outer circumferential surface of the roller and the front wall of the pocket, but of course in other embodiments, the tangent value of the inclination angle of the front wall may also be greater than or less than the coefficient of friction between the outer circumferential surface of the roller and the front wall of the pocket; the inclination angle of the rear sidewall of the pocket may satisfy a tangent value greater than a coefficient of friction between the outer circumferential surface of the roller and the rear sidewall of the pocket, and of course, in other embodiments, the inclination angle of the rear sidewall of the pocket may also satisfy a tangent value equal to a coefficient of friction between the outer circumferential surface of the roller and the rear sidewall of the pocket, or the rear sidewall may be other inclination angles.
In the specific embodiment of the retainer for the cylindrical roller bearing of the present invention, the structure of the retainer for the cylindrical roller bearing is the same as that of the retainer in the above embodiment of the cylindrical roller bearing, and details are not repeated.
Claims (8)
1. Cylindrical roller bearing holder, including the axis along the annular body that extends in the left and right directions and radially link up the pocket hole that sets up on annular body, its characterized in that: the projection shape of the side wall of the pocket in the radial direction is a frame shape with two narrow ends and a wide middle part, the wide middle part and the narrow two ends of the frame shape form a step, the narrow two ends of the pocket are provided with two end side walls which are opposite in the circumferential direction and are used for being in sliding fit with the outer peripheral surfaces of the small-diameter sections at the two ends of the stepped shaft-shaped roller with the thick middle part and the thin two ends, and the wide middle part of the pocket is provided with two middle side walls which are opposite in the circumferential direction and are used for being in clearance fit with the outer peripheral surfaces of the large-diameter sections at the middle of the stepped shaft-shaped roller with the thick middle; the rear side wall of the end side walls of the pocket is inclined in the radial direction from inside to outside towards the positive direction of the rotation direction of the annular body; the tangent value of the inclination angle of the rear side wall of the end side walls of the pocket is equal to or greater than the friction coefficient between the outer peripheral surface of the roller and the rear side wall of the pocket.
2. The cylindrical roller bearing cage of claim 1, wherein: the width of both end portions of the pocket is the same.
3. The cylindrical roller bearing cage of claim 1 or 2, wherein: the preceding lateral wall in the end lateral wall of pocket is in the positive slope of the direction of rotation of the cyclic annular body of outside from inside in the radial direction.
4. The cylindrical roller bearing cage of claim 3, wherein: the tangent value of the inclination angle of the front wall of the end side walls of the pocket is equal to the coefficient of friction between the outer circumferential surface of the roller and the front wall of the pocket.
5. Cylindrical roller bearing, including inner circle, outer lane and holder, the holder includes the axis along the annular body that extends in the left and right sides direction and sets up the pocket hole on the annular body, is equipped with roller, its characterized in that in the pocket hole: the roller is a stepped shaft-shaped roller with a thick middle and thin two ends, the projection shape of the side wall of the pocket in the radial direction is a frame shape which is matched with the shape of the roller and has two narrow ends and a wide middle, the wide middle part of the frame shape and the narrow two ends form a step, the narrow two ends of the pocket are provided with two end side walls which are opposite in the circumferential direction and are used for being in sliding fit with the outer peripheral surfaces of the small-diameter sections at the two ends of the stepped shaft-shaped roller with the thick middle and thin two ends, and the wide middle part of the pocket is provided with two middle side walls which are opposite in the circumferential direction and are used for being in clearance fit with the outer peripheral surfaces of the large-diameter sections at the middle of the stepped shaft-shaped roller; the rear side wall of the end side walls of the pocket is inclined in the radial direction from inside to outside towards the positive direction of the rotation direction of the annular body; the tangent value of the inclination angle of the rear side wall of the end side walls of the pocket is equal to or greater than the friction coefficient between the outer peripheral surface of the roller and the rear side wall of the pocket.
6. Cylindrical roller bearing according to claim 5, characterized in that: the diameters of the thinner end portions of the stepped shaft-shaped rollers are the same.
7. Cylindrical roller bearing according to claim 5 or 6, characterized in that: the preceding lateral wall in the end lateral wall of pocket is in the positive slope of the direction of rotation of the cyclic annular body of outside from inside in the radial direction.
8. Cylindrical roller bearing according to claim 7, characterized in that: the tangent value of the inclination angle of the front wall of the end side walls of the pocket is equal to the coefficient of friction between the outer circumferential surface of the roller and the front wall of the pocket.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710094023.7A CN108457986B (en) | 2017-02-21 | 2017-02-21 | Cylindrical roller bearing and retainer thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710094023.7A CN108457986B (en) | 2017-02-21 | 2017-02-21 | Cylindrical roller bearing and retainer thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108457986A CN108457986A (en) | 2018-08-28 |
| CN108457986B true CN108457986B (en) | 2020-04-07 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201710094023.7A Active CN108457986B (en) | 2017-02-21 | 2017-02-21 | Cylindrical roller bearing and retainer thereof |
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| CN (1) | CN108457986B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109469686B (en) * | 2018-12-26 | 2024-01-30 | 江苏南方精工股份有限公司 | Outer ring capable of correcting gesture in advance when roller enters engagement and one-way clutch thereof |
| CN113107980B (en) * | 2021-05-11 | 2023-01-17 | 河南科技大学 | Cylindrical roller bearing and retainer thereof |
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2017
- 2017-02-21 CN CN201710094023.7A patent/CN108457986B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3429626A (en) * | 1965-11-24 | 1969-02-25 | Schaeffler Ohg Industriewerk | Bearing for a structural element rotating about a shaft and engageable therewith |
| DE2263223A1 (en) * | 1972-12-23 | 1974-07-11 | Teldix Gmbh | ROLLER BEARING WITH CAGE |
| CN202883706U (en) * | 2012-09-10 | 2013-04-17 | 洛阳百思特精密机械制造有限公司 | Inner-ring-free filling cylindrical roller bearing |
| CN203979133U (en) * | 2014-07-31 | 2014-12-03 | 黄石人本轴承有限公司 | Without outer shroud ladder roller bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108457986A (en) | 2018-08-28 |
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