CN111981036A - Multi-row thrust cylindrical roller bearing with high bearing capacity and long service life - Google Patents
Multi-row thrust cylindrical roller bearing with high bearing capacity and long service life Download PDFInfo
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- CN111981036A CN111981036A CN202010969218.3A CN202010969218A CN111981036A CN 111981036 A CN111981036 A CN 111981036A CN 202010969218 A CN202010969218 A CN 202010969218A CN 111981036 A CN111981036 A CN 111981036A
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- bearing
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- cylindrical roller
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/30—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for axial load mainly
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/30—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for axial load mainly
- F16C19/305—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for axial load mainly consisting of rollers held in a cage
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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
- F16C33/46—Cages for rollers or needles
- F16C33/48—Cages for rollers or needles for multiple rows of rollers or needles
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
A multi-row thrust cylindrical roller bearing with high bearing capacity and long service life comprises a seat ring, a shaft ring, cylindrical rollers and a retainer, wherein a plurality of pockets with different lengths are distributed on the retainer in a staggered mode along the radial direction, and one or more cylindrical rollers are placed in each pocket along the radial direction. The cage adopts the pocket layout with different lengths and staggered distribution, breaks the frame limitation and the interval limitation of the existing cage pocket layout, increases the arrangement quantity of the cylindrical rollers to the maximum extent, and improves the bearing load of the bearing. The invention improves the utilization rate of the roller path, and has the progressive significance of dispersing the bearing load of each cylindrical roller on the roller path surface and preventing the roller path surface from losing efficacy due to over fatigue; on the other hand, the stress concentration of the raceway surface between the bearing surface and the non-bearing surface is avoided, so that the service life of the raceway is greatly prolonged. In addition, the invention also solves the problem of friction between the cylindrical rollers and the pockets and between the cylindrical rollers in the pockets, and reduces the friction torque of the bearing.
Description
Technical Field
The invention relates to the technical field of bearings, in particular to a high-bearing long-service-life multi-row thrust cylindrical roller bearing.
Background
The cylindrical roller thrust bearing is a rolling bearing for bearing axial load and consists of a race, a shaft ring, cylindrical rollers and a retainer. The thrust roller bearing is classified into a one-way thrust roller bearing and a multi-way thrust roller bearing according to a thrust load direction, or into a single-row thrust roller bearing, a double-row thrust roller bearing and a multi-row thrust roller bearing according to the number of roller rows. The thrust cylindrical roller bearing is mainly applied to low-speed and heavy-load working occasions, such as: screw-down mechanisms of engineering machinery and metallurgical machinery, etc.
High bear long-life multiseriate thrust cylindrical roller bearing and be used for the axial to bear the higher occasion of requirement, generally be biserial thrust cylindrical roller bearing, a plurality of pocket of equipartition on the holder, two are listed as roller diameter unanimity, and length equals or one length is short crisscross to be distributed, places in the pocket of holder. Large and super-huge bearings generally adopt metal solid cages, and the cages also have several structures: a monolithic structure or a two-half combined structure; the pocket holes of the whole structure are milled and processed by adopting square holes, the two half combined structures comprise a retainer seat, a retainer cover, a pin or a screw, and the pocket holes are in cylindrical arc shapes and are drilled and processed.
Because the inner and outer ends of the cylindrical roller have a speed difference, the ratio of the height to the diameter of the cylindrical roller is not suitable to be too large. In the case of using the same cylindrical rollers, the axial load of the thrust cylindrical roller bearing depends on the number of the cylindrical rollers, and the more the cylindrical rollers are arranged, the greater the axial load can be carried. Therefore, more cylindrical rollers are arranged in a limited space as much as possible, and the method is the most effective method for improving the axial bearing load of the thrust cylindrical rollers. A common single-row or high-bearing long-service-life multi-row thrust cylindrical roller bearing adopts a single-row or multi-row raceway to support cylindrical rollers, and the method has the advantages that on one hand, the utilization rate of the raceway is low, and on the other hand, the service life of the raceway is short. Thus, increasing the utilization of the raceway is also a weight consideration.
Disclosure of Invention
In order to overcome the defects in the background art, the invention discloses a multi-row thrust cylindrical roller bearing with high bearing capacity and long service life, which aims to increase the number of the arranged cylindrical rollers and improve the bearing load of the bearing; the utilization rate of the roller path is improved, and the service life of the roller path is prolonged.
In order to realize the purpose, the following technical scheme is adopted:
a multi-row thrust cylindrical roller bearing with high bearing capacity and long service life comprises a seat ring, a shaft ring, cylindrical rollers and a retainer, wherein a plurality of pockets with different lengths are distributed on the retainer in a staggered mode along the radial direction, and one or more cylindrical rollers are placed in each pocket along the radial direction.
As a further improvement of the invention, the pockets on the cage are divided into two types, one is a long pocket and the other is a short pocket; at least two cylindrical rollers are arranged in the long pocket along the radial direction, and one cylindrical roller is arranged in the short pocket along the radial direction.
As a further improvement of the invention, the number of the long pockets is four, and the pockets are distributed in a cross shape; the short pockets are distributed in an inner layer and an outer layer, the outer layer is eight, the inner layer is four, and twelve short pockets are distributed among four long pockets at intervals.
As a further improvement of the invention, the rolling area of the cylindrical rollers in the long pockets on the raceway surface and the rolling area of the cylindrical rollers in the short pockets on the raceway surface are overlapped in a crossing manner.
As a further improvement of the invention, two positioning surfaces are arranged on the retainer, wherein one positioning surface is in contact positioning with the inner circular surface of the shaft ring, and the other positioning surface is in contact positioning with the raceway surface of the shaft ring.
As a further improvement of the invention, the shape of the pocket is approximately rectangular, and the top corners of the rectangle are provided with overtravel grooves.
As a further development of the invention, the end of the cylindrical roller facing the outer diameter of the cage is provided with a ball base surface.
As a further improvement of the invention, locking points for preventing the cylindrical rollers from falling out are chiselled on the pockets.
Due to the adoption of the technical scheme, compared with the background technology, the invention has the following beneficial effects:
the retainer of the invention adopts the pocket layout with different lengths and staggered distribution, breaks the frame limitation and the interval limitation of the existing retainer pocket layout, increases the arrangement quantity of the cylindrical rollers to the maximum extent, improves the bearing load of the bearing and has creativity.
The invention improves the utilization rate of the roller path, and has the progressive significance of dispersing the bearing load of each cylindrical roller on the roller path surface and preventing the roller path surface from losing efficacy due to over fatigue; on the other hand, the stress concentration of the raceway surface between the bearing surface and the non-bearing surface is avoided, so that the service life of the raceway is greatly prolonged.
In addition, the invention also solves the problem of friction between the cylindrical rollers and the pocket and between the cylindrical rollers in the pocket, and reduces the friction torque of the bearing.
Drawings
FIG. 1 is a schematic structural diagram of the present invention.
Fig. 2 is a schematic view of the distribution of pockets on the cage.
Fig. 3 is a schematic view showing the cylindrical rollers being put into the long and short pockets.
Fig. 4 is a sectional structure diagram of the cage.
Fig. 5 is a schematic view of the cross-sectional structure E-E in fig. 3.
Fig. 6 is a schematic structural view of a cylindrical roller.
In the figure: 1. a seat ring; 2. a shaft ring; 3. a cylindrical roller; 31. a ball base surface; 4. a holder; 41. a long pocket; 42. a short pocket; 43. positioning the surface; 44. and (4) locking points.
Detailed Description
Preferred embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood by those skilled in the art that these embodiments are only for explaining the technical principle of the present invention, and are not intended to limit the scope of the present invention. It should be noted that the terms "center", "upper", "lower", "left", "right", "inner", "outer", etc., indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience in describing the present invention and simplifying the description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present invention.
A high-bearing long-life multi-row thrust cylindrical roller bearing is shown in figure 1 and comprises a race 1, a shaft ring 2, cylindrical rollers 3 and a retainer 4. Because the bearing belongs to a large-scale bearing, the retainer 4 adopts a whole copper alloy circular plate as a matrix of the retainer 4, and the copper alloy matrix has better self-lubricating property and is matched with the cylindrical rollers 3 in a soft and hard way, so that the cylindrical rollers 3 can be better protected.
As shown in fig. 2, a plurality of pockets with different lengths are milled on the base body along the radial direction in a staggered manner, the pockets are approximately rectangular, and the four vertex angles of the rectangle are provided with overrun grooves which are used for clearing the fillets left at the vertex angles of the milling cutter so as to prevent the fillets from interfering with the cylindrical roller 3. In the present embodiment, the pockets on the cage 4 are divided into two types, one being the long pockets 41 and one being the short pockets 42. The number of the long pockets 41 is four, and the pockets are uniformly distributed in four directions, namely, front, rear, left and right. The short pockets 42 are divided into two layers in the radial direction, eight short pockets 42 are provided near the outer layer, and are circumferentially spaced apart from the four long pockets 41; there are four short pockets 42 adjacent the inner layer, again circumferentially spaced. As can be seen from the figure, circles passing through the centers of the outer short pockets 42, the long pockets 41 and the inner short pockets 42 with the center of the cage 4 as a circular dot have different diameters d1, d2 and d 3. The pocket layout with different lengths and staggered distribution breaks the frame limitation and the interval limitation of the existing pocket layout, increases the arrangement quantity of the cylindrical rollers 3 to the maximum extent, and improves the bearing load of the bearing.
As shown in fig. 3, two cylindrical rollers 3 are disposed in the long pocket 41 in the radial direction, and one cylindrical roller 3 is disposed in the short pocket 42 in the radial direction. As can be seen from the figure, the cylindrical rollers 3 inside the long pockets 41 that are close to the outer side have the same rolling area on the raceway surface as the cylindrical rollers 3 inside the outer layer short pockets 42, but the cylindrical rollers 3 inside the long pockets 41 that are close to the inner side have not all the same rolling area on the raceway surface as the cylindrical rollers 3 inside the inner layer short pockets 42. That is, the rolling areas of the two cylindrical rollers 3 in the long pockets 41 on the raceway surface and the rolling areas of the cylindrical rollers 3 in the inner and outer short pockets 42 on the raceway surface are overlapped with each other, so that the effective areas of the raceways are increased as the race 1 and the race 2 supporting the respective cylindrical rollers 3, and the raceway utilization ratio is improved. The bearing load of each cylindrical roller 3 on the raceway surface is dispersed, failure of the raceway surface due to over fatigue is prevented, and stress concentration of the raceway surface between the bearing surface and the non-bearing surface is avoided. As is well known, in the conventional multi-row cylindrical roller thrust 3 bearing, the rolling areas of the roller bearings in each row are a series of concentric circular belts, and the rolling areas do not overlap with each other, so that the failure of the rolling areas due to over fatigue is easily caused because of high concentration of load bearing. On the other hand, the rolling area is a bearing surface, and the adjacent non-rolling area is a non-bearing surface, and a crack is generated at the boundary between the bearing surface and the non-bearing surface due to stress concentration, thereby causing bearing scrap.
In order to position the retainer 4, as shown in fig. 4, two positioning surfaces 43 are provided on the retainer 4, wherein one positioning surface 43 contacts with the inner circumferential surface of the collar 2 to radially position the retainer 4; the other positioning surface 43 is positioned in contact with the raceway surface of the race 2 for axially positioning the cage 4.
In order to prevent the cylindrical rollers 3 from falling out of the short and long pockets 42 and 41, as shown in fig. 5, after the cylindrical rollers 3 are placed in the pockets, locking points 44 for preventing the cylindrical rollers 3 from falling out are chiseled on the upper and lower surfaces of the pockets.
The rotation of the cylindrical rollers 3 in the short pockets 42 or the long pockets 41, which have both rotation and revolution, generates rotational friction on one end surface of the short pockets 42 or the long pockets 41 near the outer side. The end surfaces of the existing cylindrical rollers 3 are all planes, the friction surfaces of the planes are large, and the resistance moment caused by friction is also large. In order to reduce this resistance torque, the solution is further developed, as shown in fig. 6, in which a ball base surface 31 is provided at an end of the cylindrical roller 3 facing the outer diameter of the cage 4. The ball base surface 31 changes the face-to-face friction of the cylindrical roller 3 with the short pocket 42 or the long pocket 41 into point-to-face friction because the frictional force arm is sharply reduced, thereby greatly reducing the moment of resistance caused by the friction. Another positive aspect is that the cylindrical rollers 3 near the inner side in the long pocket 41 are pressed against the ball base surface 31 on the cylindrical rollers near the outer side on the inner end plane of the cylindrical rollers 3, which can also greatly reduce the friction torque between the two cylindrical rollers 3, and solve the problem of friction between the two cylindrical rollers 3 in the long pocket 41.
It is to be noted that, in the present embodiment, two cylindrical rollers 3 are disposed in the long pocket 41 in the radial direction, but it is not an obstacle to disposing three or more cylindrical rollers 3 in the long pocket 41 in the radial direction, and likewise, two or more cylindrical rollers 3 may be disposed in the short pocket 42 in the radial direction.
The present invention is not described in detail in the prior art. Although embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, the scope of which is defined in the appended claims and their equivalents.
Claims (8)
1. The multi-row thrust cylindrical roller bearing with high bearing capacity and long service life comprises a seat ring, a shaft ring, cylindrical rollers and a retainer, and is characterized in that a plurality of pockets with different lengths are distributed on the retainer in a staggered mode along the radial direction, and one or more cylindrical rollers are placed in each pocket along the radial direction.
2. A high-load-bearing long-life multi-row thrust cylindrical roller bearing as set forth in claim 1, wherein: the pockets on the retainer are divided into two types, one is a long pocket and the other is a short pocket; at least two cylindrical rollers are arranged in the long pocket along the radial direction, and one cylindrical roller is arranged in the short pocket along the radial direction.
3. A high-load-bearing long-life multi-row thrust cylindrical roller bearing as set forth in claim 2, wherein: the number of the long pockets is four, and the long pockets are distributed in a cross shape; the short pockets are distributed in an inner layer and an outer layer, the outer layer is eight, the inner layer is four, and twelve short pockets are distributed among four long pockets at intervals.
4. A high-load-bearing long-life multi-row thrust cylindrical roller bearing as set forth in claim 2, wherein: the rolling area of the cylindrical roller in the long pocket hole on the raceway surface is overlapped with the rolling area of the cylindrical roller in the short pocket hole on the raceway surface in a crossed manner.
5. A high-load-bearing long-life multi-row thrust cylindrical roller bearing as set forth in claim 1, wherein: two positioning surfaces are arranged on the retainer, wherein one positioning surface is in contact positioning with the inner circle surface of the shaft ring, and the other positioning surface is in contact positioning with the raceway surface of the shaft ring.
6. A high-load-bearing long-life multi-row thrust cylindrical roller bearing as set forth in claim 1, wherein: the shape of the pocket is rectangular, and an overtravel groove is arranged at the vertex angle of the rectangle.
7. A high-load-bearing long-life multi-row thrust cylindrical roller bearing as claimed in any one of claims 1 to 6, wherein: one end of the cylindrical roller facing the outer diameter of the retainer is provided with a ball base surface.
8. The high-load-bearing long-life multi-row thrust cylindrical roller bearing of claim 7, wherein: and locking points for preventing the cylindrical rollers from falling out are chiselled and printed on the pockets.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010969218.3A CN111981036A (en) | 2020-09-15 | 2020-09-15 | Multi-row thrust cylindrical roller bearing with high bearing capacity and long service life |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010969218.3A CN111981036A (en) | 2020-09-15 | 2020-09-15 | Multi-row thrust cylindrical roller bearing with high bearing capacity and long service life |
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| Publication Number | Publication Date |
|---|---|
| CN111981036A true CN111981036A (en) | 2020-11-24 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010969218.3A Pending CN111981036A (en) | 2020-09-15 | 2020-09-15 | Multi-row thrust cylindrical roller bearing with high bearing capacity and long service life |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113623316A (en) * | 2021-04-28 | 2021-11-09 | 洛阳轴承研究所有限公司 | Thrust roller bearing retainer and thrust roller bearing |
| US11867228B2 (en) | 2021-02-08 | 2024-01-09 | Ratier-Figeac Sas | Thrust bearings |
-
2020
- 2020-09-15 CN CN202010969218.3A patent/CN111981036A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11867228B2 (en) | 2021-02-08 | 2024-01-09 | Ratier-Figeac Sas | Thrust bearings |
| CN113623316A (en) * | 2021-04-28 | 2021-11-09 | 洛阳轴承研究所有限公司 | Thrust roller bearing retainer and thrust roller bearing |
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