CN112460142A

CN112460142A - Self-aligning roller bearing for vibration machinery

Info

Publication number: CN112460142A
Application number: CN202011422789.1A
Authority: CN
Inventors: 蔡梅贵; 蔡玉铨; 蔡欣怡; 张明远; 蔡培峰
Original assignee: Shandong Yujie Bearing Manufacture Co ltd
Current assignee: Shandong Yujie Bearing Manufacture Co ltd
Priority date: 2020-12-08
Filing date: 2020-12-08
Publication date: 2021-03-09

Abstract

The invention discloses a self-aligning roller bearing for vibration machinery, which belongs to the technical field of bearings and comprises an outer ring, an inner ring and two rows of rollers, wherein the rollers are symmetrical spherical rollers, the opposite end surfaces of the two rows of rollers are both arranged as spherical base surfaces, the self-aligning roller bearing further comprises a floating middle check ring arranged between the two rows of rollers, the inner diameter surface of a retainer body is guided by the outer diameter surface of the floating middle check ring, a plurality of oil grooves are formed in the inner diameter surface of the retainer body between every two adjacent pockets of claws, and the oil grooves axially penetrate through the retainer body. The self-aligning roller bearing for the vibrating machinery disclosed by the invention can allow higher total load of the roller, simplifies the structure of the inner ring, can form an effective lubricating oil film by a small gap between the inner diameter of the main body of the retainer and the outer diameter of the floating middle retainer ring, increases the height of the radial section of the retainer so as to increase the wrapping of pocket holes on the diameter of the roller, and has the advantages of strong vibration resistance, good stability and prolonged service life by more than 3 times.

Description

Self-aligning roller bearing for vibration machinery

Technical Field

The invention relates to a self-aligning roller bearing for a vibrating machine, and belongs to the technical field of bearings.

Background

In recent years, with the rapid development of metallurgical mines, road engineering and the like, equipment applied to the metallurgical mines, the road engineering and the like, such as a vibrating feeder, a vibrating conveyor, a vibrating screen, a vibrating ball mill, a vibrating road roller and the like, has also been rapidly developed. Currently, the bearings used in these devices are self-aligning roller bearings of the general MB and MA structure. These devices are generally operated in the open air, and therefore the bearings are inevitably affected by temperature differences and dust. In addition, due to the influence of the processing mode of the equipment, the bearing always works in the vibration impact load, the roller cannot be in a balanced running state along with the frequent rapid acceleration and rapid deceleration of the bearing in the running process of the bearing, the roller deflection and the eccentric load of the roller path are caused, the pocket surface of the retainer and the rolling surface of the roller often collide, the retainer is easy to break, copper powder is bonded on the rolling surface of the rolling element, the surface of the outer roller path, the surface of the inner roller path and the like, and the bearing is abnormally and prematurely damaged.

Fig. 1 and 2 show a self-aligning roller bearing of a general MA (cage outer guide) and MB (cage inner guide) structure, respectively, and the two types of rollers mostly adopt an asymmetric roller with a ball base as shown in fig. 3 (Dw2< Dw1) and an inner ring structure as shown in fig. 4. The stress condition of the roller is shown in figure 5 (the stress conditions of the rollers of the MA structure and the MB structure are the same, so that the stress condition of the roller of the MB structure is only shown). As shown in fig. 5, in the MA and MB structures, since the contact angles α and β between the rollers (3) and the outer ring (1) and the inner ring 2 are different from each other, the supporting forces N1 and N2 of the rollers (3) by the outer ring (1) and the inner ring (2) cannot be balanced, and therefore, the supporting force N3 of the retainer ring (5) fixed to the inner ring 2 against the spherical surface of the rollers (3) is inevitably required to balance the supporting forces N1 and N2 of the outer ring (1) and the inner ring against the rollers. Because the ball base surface of the roller (3) is supported by the supporting force N3 of the fixed middle check ring (5), the sliding friction between the ball base surface of the roller (3) and the fixed middle check ring (5) is serious, so that the temperature rise of the bearing is increased, the hardness is reduced, and the bearing is locked or damaged in advance. Meanwhile, as shown in fig. 6, the load distribution on the rolling surface of the asymmetric roller (3) with the spherical basal plane is uneven, stress concentration can be caused at the small-diameter end of the roller (3), and the bearing capacity is limited by the stress peak value.

The above description is included in the technical recognition scope of the inventors, and does not necessarily constitute the prior art.

Disclosure of Invention

The invention provides a self-aligning roller bearing for a vibrating machine, which aims to solve the problems in the prior art, can allow higher total load of rollers, simplifies the structure of an inner ring, can form an effective lubricating oil film by a fine gap between the inner diameter of a main body of a retainer and the outer diameter of a floating middle check ring, and increases the height of the radial section of the retainer so as to increase the wrapping of pocket holes on the diameters of the rollers.

The invention adopts the following technical scheme to realize the purpose:

a self-aligning roller bearing for a vibrating machine comprises an outer ring, an inner ring and two rows of rollers, wherein each row of rollers is limited between the outer ring and the inner ring through a retainer, and the outer ring is provided with a plurality of oil guide holes which penetrate through the outer ring along the radial direction of the outer ring;

the rollers are symmetrical spherical rollers, and the opposite end surfaces of the two rows of rollers are arranged as spherical base surfaces;

the self-aligning roller bearing also comprises a floating middle check ring arranged between two rows of rollers, and the inner diameter surface of the floating middle check ring is in clearance fit with the outer diameter surface of the inner ring;

the retainer comprises an annular retainer body and a plurality of pocket claws arranged on one axial side of the retainer body in a hanging mode, two adjacent pocket claws and the retainer body form a pocket together in a surrounding mode, and each row of rollers are assembled in the pocket holes of the corresponding retainer respectively;

the inner diameter surface of the retainer body is guided by the outer diameter surface of the floating middle retainer ring, a plurality of oil grooves are formed in the inner diameter surface of the retainer body between every two adjacent pocket claws, and the oil grooves penetrate through the retainer body in the axial direction;

the distance between the outer diameter surface and the inner diameter surface of each pocket jaw is 0.45-0.55 times the diameter of the roller.

Optionally, the arc length of the outer diameter of each pocket claw is 1.1-1.5 times of the arc length of the inner diameter of each pocket claw.

Optionally, the distance between the end faces of the two cages is 0.5-1.0 mm.

Optionally, the distance between the inner diameter surface of the floating middle retainer ring and the outer diameter surface of the inner ring is 0.15-0.6 mm.

Optionally, a gap between the inner diameter surface of the retainer body and the outer diameter surface of the floating middle retainer ring is 0.2-0.7 mm.

Optionally, two ends of the inner ring are respectively provided with an annular flange, and the flange surrounds the outer diameter surface of the inner ring along the circumferential direction of the inner ring.

Optionally, the retainer is made of aluminum bronze material, the tensile strength is larger than or equal to 460Mpa, the elongation is larger than or equal to 20%, the hardness is 102-142HBW, and the friction coefficient is 0.07-0.12.

Optionally, the end face of the floating middle retainer ring opposite to the roller is a conical surface.

Optionally, the wall surface of the pocket claw is in surface contact with the rolling surface of the roller.

Optionally, the hardness of the inner ring is more than or equal to 62 HRC.

Benefits of the present application include, but are not limited to:

the self-aligning roller bearing for the vibrating machinery provided by the invention has the advantages of strong vibration resistance, good stability and longer service life by more than 3 times compared with the common type. Specifically, the roller is changed into a symmetrical roller structure with a spherical base surface from an asymmetrical roller with a spherical base surface, so that the load distribution on the outer diameter of the roller is more even, and higher total load of the roller is allowed; the floating middle check ring does not bear axial force any more, the floating middle check ring is in clearance fit with the inner ring, and the inner diameter surface of the retainer body is guided by the outer diameter surface of the floating middle check ring, so that the structure of the inner ring is simplified, and the inner ring can be conveniently turned and ground; the inner diameter surface of the retainer body is provided with the oil groove, so that lubricating oil can easily enter a small gap between the inner diameter of the retainer body and the outer diameter of the floating middle check ring to form an effective lubricating oil film, the friction between the inner diameter of the retainer body and the outer diameter of the floating middle check ring is reduced, the temperature rise of a bearing is low, and the bearing is impact-resistant; the radial section height of the retainer is increased, so that the wrapping of the pocket holes on the diameter of the roller is increased, the rigidity of the retainer is enhanced by more than 2 times, the bearing has strong rigidity and large bearing capacity; and the hardness of the inner ring is increased, so that the wear resistance of the inner raceway is improved by more than one time.

Drawings

The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the application and together with the description serve to explain the application and not to limit the application. In the drawings:

fig. 1 is a schematic structural view of a conventional external guide MA type self-aligning roller bearing;

fig. 2 is a schematic structural view of a conventional inner guide MB type self-aligning roller bearing;

fig. 3 is a schematic structural diagram of an asymmetric roller with a ball base surface in a conventional MA or MB type self-aligning roller bearing;

FIG. 4 is a schematic structural diagram of an inner ring of a conventional MA or MB type self-aligning roller bearing;

fig. 5 is a schematic diagram of a stress condition of a roller in a conventional MB-type self-aligning roller bearing;

fig. 6 is a schematic view of load distribution on a rolling surface of an asymmetric roller with a ball base surface in a conventional MA or MB type self-aligning roller bearing;

FIG. 7 is a schematic structural view of a self-aligning roller bearing for a vibration machine according to the present invention;

FIG. 8 is a schematic structural view of a roller in the self-aligning roller bearing for vibration machinery according to the present invention;

FIG. 9 is a schematic view showing the distribution of the load on the rolling surfaces of the rollers in the self-aligning roller bearing for vibration machinery according to the present invention;

FIG. 10 is a schematic view of a stress condition of a roller in the self-aligning roller bearing for the vibration machine according to the present invention;

FIG. 11 is a schematic structural view of a floating middle retainer ring in the self-aligning roller bearing for the vibration machine according to the present invention;

FIG. 12 is a schematic structural view of an inner ring of the self-aligning roller bearing for vibration machinery according to the present invention;

fig. 13 is a schematic structural view of a retainer in floating in a self-aligning roller bearing for a vibration machine according to the present invention;

FIG. 14 is a schematic sectional view taken along line A-A of FIG. 13;

fig. 15 is a schematic perspective view of a floating retainer in a self-aligning roller bearing for a vibration machine according to the present invention;

FIG. 16 is an enlarged view of the portion B of FIG. 13;

in the figure, 100, outer ring; 110. an oil guide hole; 200. an inner ring; 210. blocking edges; 300. a roller; 310. a ball base surface; 400. a holder; 410. a holder body; 420. covering claws; 430. an oil sump; 500. a floating middle retainer ring; 510. a conical surface.

Detailed Description

In order to clearly explain the technical features of the present invention, the following detailed description of the present invention is provided with reference to the accompanying drawings.

It should be noted that in the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those described herein. Therefore, the scope of the invention is not limited by the specific embodiments disclosed below.

As shown in fig. 7, the self-aligning roller bearing for a vibration machine according to the present invention includes an outer ring 100, an inner ring 200, and two rows of rollers 300, each row of rollers 300 being defined between the outer ring 100 and the inner ring 200 by a cage 400. Specifically, the inner diameter surface of the outer ring 100 is provided with a spherical outer raceway, the outer diameter surface of the inner ring 200 is provided with two inner raceways which are inclined in opposite directions by a certain angle, and the two rows of rollers 300 share the outer raceway on the outer ring 100 and are respectively accommodated between the outer raceway and the corresponding inner raceway.

As shown in fig. 8, in the present invention, the rollers 300 are symmetrical spherical rollers, and the opposite end surfaces of the two rows of rollers 300 are provided as ball base surfaces 310. The spherical roller means that the rolling surface of the roller is spherical, and the rolling surface of the symmetrical spherical roller is symmetrical about a plane which passes through the axial center of the roller and is perpendicular to the axis of the roller. In the present invention, after the roller 300 is changed to a symmetrical spherical structure with spherical base surface, as shown in fig. 9, the load distribution on the outer diameter of the roller 300 is more even, allowing a higher total load of the roller 300, increasing the load capacity of the bearing, and further increasing the bearing life.

Further, the stress of the roller 300 in the self-aligning roller bearing for the vibrating machine provided by the invention is shown in fig. 10, as shown in fig. 10, the contact points of the roller 300 and the inner raceway and the outer raceway are on a straight line, and the supporting forces of the inner raceway and the outer raceway on the roller 300 are balanced. Therefore, the middle retainer ring between the two rows of rollers 300 does not bear axial force any more, and the bearing temperature rise increase and early damage caused by friction between the ball base surface 310 of the rollers 300 and the middle retainer ring are avoided. Meanwhile, the middle retainer ring no longer bears the axial force, so as shown in fig. 7 and fig. 11, in the self-aligning roller bearing provided by the invention, the floating middle retainer ring 500 is arranged between two rows of rollers 300, the inner diameter surface of the floating middle retainer ring 500 is in clearance fit with the outer diameter surface of the inner ring 200, the floating middle retainer ring 500 is adopted to replace the original structure that the middle retainer ring is fixed on the inner ring 200, and the structure of the inner ring 200 is shown in fig. 12, so that the structure of the inner ring 200 is simplified, and the inner ring 200 can be conveniently turned and ground.

Further, referring again to fig. 11, the end surface of the floating retainer ring 500 opposite the roller 300 is tapered 510.

Further, as shown in fig. 13 to 15, the cage 400 of the present invention includes an annular cage body 410 and a plurality of pockets 420 overhanging one side of the cage body 410 in the axial direction, two adjacent pockets 420 and the cage body 410 together define a pocket, and each row of rollers 300 is respectively fitted in the pockets of the corresponding cage 400.

Specifically, the wall surface of the pocket claw 420 is in surface contact with the rolling surface of the roller 300, and the cage main body 410 and the pocket claw 420 are integrally formed as the stamped cage 400.

Further, in the present invention, both ends of the inner ring 200 are respectively provided with an annular rib 210, and the rib 210 surrounds the outer diameter surface of the inner ring 200 along the circumferential direction of the inner ring 200. When the vibration machine works, the self-aligning roller bearing works under vibration impact load, the roller 300 is often accelerated and decelerated rapidly and is easy to deflect in the running process, in order to control the posture of the roller 300 and avoid the deviation of the roller 300, the invention adopts the retainer 400 and the floating middle retainer ring 500 to restrict the posture of the roller 300, and in order to stabilize the retainer 400, the inner diameter surface of the retainer main body 410 is guided by the outer diameter surface of the floating middle retainer ring 500.

In order to reduce friction between the structures, the outer ring 100 is provided with a plurality of oil guide holes 110 penetrating the outer ring 100 in the radial direction of the outer ring 100, and the oil guide holes 110 are used for guiding lubricating oil between the inner ring 200 and the outer ring 100. Since the inner diameter surface of the retainer body 410 is guided by the outer diameter surface of the floating intermediate retainer 500, and the clearance between the inner diameter surface of the retainer body 410 and the outer diameter surface of the floating intermediate retainer 500 is about 0.2-0.7mm, preferably 0.4-0.6mm, it is difficult for the lubricant to enter between the inner diameter of the retainer body 410 and the outer diameter of the floating intermediate retainer 500, and it is more difficult to form a lubricant film. Therefore, in the invention, the inner diameter surface of the retainer body 410 between two adjacent pocket claws 420 is provided with a plurality of oil grooves 430, and the oil grooves 430 axially penetrate through the retainer body 410, so that lubricating oil easily enters a small gap between the inner diameter of the retainer body 410 and the outer diameter of the floating middle check ring 500 to form an effective lubricating oil film, thereby enhancing the lubricating performance of a bearing and reducing the friction between the inner diameter of the retainer body 410 and the outer diameter of the floating middle check ring 500.

Specifically, the oil groove 430 is semicircular in cross section perpendicular to the axial direction of the cage body 410.

Further, as shown in FIG. 16, the distance D between the outer diameter surface and the inner diameter surface of each pocket jaw 420 in the present invention is 0.45 to 0.55 times the diameter of the roller 300. So set up, with the external diameter increase of holder 400, the internal diameter reduces, has increased the radial cross-section height of holder 400 and has made the parcel of pocket hole to roller 300 diameter increase, and holder 400 rigidity reinforcing is more than 2 times.

As shown in FIG. 16, in one embodiment, each pocket jaw 420 has an outer radial arc length S1 that is 1.1-1.5 times its inner radial arc length S2.

In another embodiment, the distance between the end faces of the two cages 400 is between 0.5 and 1mm, preferably between 0.7 and 0.9 mm.

In another embodiment, the distance between the inner diameter surface of the floating intermediate collar 500 and the outer diameter surface of the inner ring 200 is 0.15 to 0.6mm, preferably 0.3 to 0.4 mm.

The retainer 400 is made of aluminum bronze, preferably ZCAI 10Fe3Mn2, the tensile strength Rm of the retainer 400 is larger than or equal to 460Mpa, the elongation is larger than or equal to 20%, the hardness 102 and 142HBW are achieved, the friction coefficient is 0.07-0.12, the dimensional accuracy and the surface roughness of the pocket claws 420 are improved, and the friction between the wall surface of the pocket claws 420 and the rolling surface of the roller 300 is reduced by more than 50%.

Because the inner ring of the self-aligning roller bearing for the vibrating machinery bears point load, namely the load is fixed and unchanged relative to the position of the inner ring, the load area is fixed and unchanged when an inner raceway on the inner ring of the self-aligning roller bearing for the vibrating machinery works, most of the conditions are concentrated in a small fan-shaped area when the inner raceway is damaged, and other areas of the inner raceway are intact. Aiming at the situation, the heat treatment process of the inner ring is improved, the inner ring is made of GCr15 or GCr18Mo materials, the hardness of the quenched and tempered inner ring is increased by 2-3HRC and reaches more than 62HRC, and the wear resistance of the inner raceway is improved by more than one time.

In the description of the present invention, it is to be understood that the terms "central," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "axial," "radial," "circumferential," and the like are used in the indicated orientations and positional relationships based on the drawings for ease of description and simplicity of description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; the connection can be mechanical connection, electrical connection or communication; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

The above-described embodiments should not be construed as limiting the scope of the invention, and any alternative modifications or alterations to the embodiments of the present invention will be apparent to those skilled in the art.

The present invention is not described in detail, but is known to those skilled in the art.

Claims

1. The utility model provides a self-aligning roller bearing for vibrating machinery, includes outer lane, inner circle and two rows of rollers, every row of roller is injectd between outer lane and inner circle through a holder respectively, be provided with a plurality of on the outer lane and radially run through the oil guide hole of outer lane, its characterized in that along the outer lane:

2. The self-aligning roller bearing for a vibration machine according to claim 1, wherein an arc length of an outer diameter of each pocket claw is 1.1 to 1.5 times as long as an arc length of an inner diameter thereof.

3. The self-aligning roller bearing for a vibration machine according to claim 1, wherein a distance between end faces of the two cages is 0.5 to 1.0 mm.

4. The self-aligning roller bearing for a vibration machine according to claim 1, wherein a distance between an inner diameter surface of the floating middle retainer and an outer diameter surface of the inner ring is 0.15 to 0.6 mm.

5. The self-aligning roller bearing for a vibration machine according to claim 1, wherein a clearance between an inner diameter surface of the cage main body and an outer diameter surface of the floating intermediate ring is 0.2 to 0.7 mm.

6. The self-aligning roller bearing for a vibration machine according to claim 1, wherein annular ribs are provided at both ends of the inner ring, respectively, and the ribs are circumferentially wound around an outer diameter surface of the inner ring along the inner ring.

7. The self-aligning roller bearing for vibration machinery as claimed in claim 1, wherein the retainer is made of an aluminum bronze material, and has a tensile strength of 460Mpa or more, an elongation of 20% or more, a hardness of 102-142HBW, and a friction coefficient of 0.07-0.12.

8. The self-aligning roller bearing for a vibration machine according to claim 1, wherein an end surface of the floating middle retainer opposite to the roller is a tapered surface.

9. The self-aligning roller bearing for a vibration machine according to claim 1, wherein a wall surface of the pocket claw is in surface contact with a rolling surface of the roller.

10. The self-aligning roller bearing for a vibration machine according to claim 1, wherein a hardness of the inner ring is not less than 62 HRC.