CN112211901A - Thrust type cylindrical roller bearing - Google Patents

Thrust type cylindrical roller bearing Download PDF

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Publication number
CN112211901A
CN112211901A CN202011034755.5A CN202011034755A CN112211901A CN 112211901 A CN112211901 A CN 112211901A CN 202011034755 A CN202011034755 A CN 202011034755A CN 112211901 A CN112211901 A CN 112211901A
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CN
China
Prior art keywords
diameter
end surface
cylindrical roller
peripheral surface
outer ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202011034755.5A
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Chinese (zh)
Inventor
刘博�
邹腊年
郭玲琼
徐飞飞
夏益锋
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shaoxing Shangyu District Institute Of Technology
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Shaoxing Shangyu District Institute Of Technology
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Filing date
Publication date
Application filed by Shaoxing Shangyu District Institute Of Technology filed Critical Shaoxing Shangyu District Institute Of Technology
Priority to CN202011034755.5A priority Critical patent/CN112211901A/en
Publication of CN112211901A publication Critical patent/CN112211901A/en
Pending legal-status Critical Current

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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
    • F16C19/34—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 both radial and axial load
    • F16C19/36—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 both radial and axial load with a single row of rollers
    • F16C19/361—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 both radial and axial load with a single row of rollers with cylindrical rollers
    • 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
    • F16C33/58—Raceways; Race rings
    • 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
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

The invention discloses a thrust type cylindrical roller bearing, which comprises an inner ring, an outer ring, a retainer and a plurality of cylindrical rollers, wherein: the retainer comprises two oppositely arranged end surface parts and a plurality of connecting bodies for connecting the two end surface parts; at least one of the inner ring and the outer ring is provided with a stopping groove at two axial ends, which correspond to the two end surfaces respectively; one end surface part is limited by the abutting groove along at least one of the radial outer side and the radial inner side of the end surface part to prevent the end surface part from being separated from the inner ring or the outer ring, and the other end surface part is limited by the abutting groove along at least one of the radial outer side and the radial inner side of the end surface part to prevent the end surface part from being separated from the inner ring or the outer ring. According to the thrust type cylindrical roller bearing provided by the invention, the inner ring or the outer ring is provided with the abutting groove, and the end surface part of the retainer is abutted against the abutting groove, so that the cylindrical roller is axially limited, and the bearing flange in the prior art is effectively replaced.

Description

Thrust type cylindrical roller bearing
Technical Field
The invention relates to the technical field of bearings, in particular to a thrust type cylindrical roller bearing.
Background
The bearing is an important part in modern mechanical equipment, the main function of the bearing is to support a mechanical rotating body, reduce the friction coefficient in the movement process and ensure the rotation precision of the mechanical rotating body, an early linear motion bearing mode is to place a row of wooden rods under a row of prying plates, the modern linear motion bearing uses the same working principle, but sometimes uses balls to replace rollers, and the simplest rotary bearing is a shaft sleeve bearing which is a bushing clamped between a wheel and a wheel shaft.
The design is replaced by a rolling bearing, namely, a plurality of cylindrical rollers are used for replacing an original lining to form a high-rigidity bearing, the cylindrical roller bearing can bear larger radial load, the flange of the inner ring or the outer ring has certain thickness, so that the bearing cannot bear larger axial load, the processing difficulty is relatively larger because the flange is arranged on the outer side, usually, a groove is formed in the peripheral surface of the inner ring or the outer ring by turning, a structure with a concave middle and two convex ends is formed, and a tool withdrawal groove is inevitably required to be processed.
Therefore, a cylindrical roller bearing without a flange is needed.
Disclosure of Invention
The invention aims to overcome the technical defects and provides a thrust type cylindrical roller bearing which is used for solving the problem that the cylindrical roller bearing in the prior art has flanges.
In order to achieve the technical purpose, the technical scheme of the invention is as follows: a thrust-type cylindrical roller bearing comprising an inner ring, an outer ring, a cage and a plurality of cylindrical rollers, wherein: the retainer comprises two annular end surface parts which are oppositely arranged and a plurality of connecting bodies which are connected with the two end surface parts, the plurality of connecting bodies are circumferentially arranged along the end surface parts, and an accommodating cavity for accommodating the cylindrical roller is formed between the adjacent connecting bodies; at least one of the inner ring and the outer ring is provided with a stopping groove at two axial ends, which correspond to the two end surfaces respectively; when the inner ring is provided with the stopping grooves, the inner sides of the two end surface parts along the radial direction are respectively abutted with the two stopping grooves; when the outer ring is provided with the stopping grooves, the outer sides of the two end surface parts along the radial direction are respectively abutted with the two stopping grooves; when the same sides of the inner ring and the outer ring are both provided with the abutting grooves, the inner sides or the outer sides of the two end surface parts along the radial direction are respectively abutted against any corresponding abutting groove and/or the two abutting grooves at the same side; the two end faces of the cylindrical roller are respectively abutted against the two end face parts.
Preferably, a rolling element is interposed between the abutting groove and the end surface portion to reduce friction when the abutting groove and the end surface portion rotate relative to each other.
Preferably, the abutting grooves are formed on both sides of the inner peripheral surface of the outer ring and are recessed radially outward.
Preferably, the abutting grooves are formed on both sides of the outer peripheral surface of the inner ring and are recessed radially inward.
Preferably, the outer diameter of each end surface in the radial direction is larger than the inner peripheral surface diameter of the outer ring and smaller than the circumferential surface diameter of the abutting groove at the outer ring, and the inner diameter of each end surface in the radial direction is larger than the outer peripheral surface diameter of the inner ring.
Preferably, the inner diameter of each end surface in the radial direction is smaller than the diameter of the outer peripheral surface of the inner ring and larger than the diameter of the peripheral surface of the abutting groove at the inner ring, and the outer diameter of each end surface in the radial direction is smaller than the diameter of the inner peripheral surface of the outer ring.
Preferably, the outer diameter of the one end surface portion in the radial direction is larger than the inner peripheral surface diameter of the outer ring and smaller than the circumferential surface diameter of the abutting groove at the outer ring, and the inner diameter of the other end surface portion in the radial direction is smaller than the outer peripheral surface diameter of the inner ring and larger than the circumferential surface diameter of the abutting groove at the inner ring.
Preferably, the diameter of the outer side of one end surface part along the radial direction is larger than the diameter of the inner circumferential surface of the outer ring and smaller than the diameter of the circumferential surface of the abutting groove at the outer ring; the diameter of the inner side of the other end face part along the radial direction is smaller than the diameter of the outer peripheral surface of the inner ring and larger than the diameter of the peripheral surface of the abutting groove at the inner ring, and the diameter of the outer side of the other end face part along the radial direction is larger than the diameter of the inner peripheral surface of the outer ring and smaller than the diameter of the peripheral surface of the abutting groove.
Preferably, the outer diameter of each end surface in the radial direction is larger than the inner peripheral surface diameter of the outer ring and smaller than the circumferential surface diameter of the abutting groove at the outer ring, and the inner diameter of each end surface in the radial direction is smaller than the outer peripheral surface diameter of the inner ring and larger than the circumferential surface diameter of the abutting groove at the inner ring.
Preferably, the retainer comprises two blocking pieces which are fixedly connected, and the two blocking pieces are close to each other to form an end surface part.
Compared with the prior art, the invention has the beneficial effects that: the inner ring or the outer ring is provided with the abutting groove, the end surface part of the retainer is abutted against the abutting groove, and the cylindrical roller is axially limited, so that the flange of the bearing in the prior art is effectively replaced, the thickness of the part bearing the radial load is not limited any more, the bearing can bear larger radial load, a tool withdrawal groove does not need to be machined, and the manufacturing process is simplified.
Drawings
Fig. 1 is a perspective view of a thrust cylindrical roller bearing embodiment 1 provided by the present invention;
FIG. 2 is an exploded view of embodiment 1 of the thrust cylindrical roller bearing provided by the present invention;
FIG. 3 is a sectional view of embodiment 1 of the thrust cylindrical roller bearing of the present invention taken along the normal plane of the axis;
FIG. 4 is a front view of embodiment 1 of the thrust cylindrical roller bearing provided by the present invention;
FIG. 5 is a partial cross-sectional view taken at A in FIG. 4;
FIG. 6 is a partial cross-sectional view at B in FIG. 4;
FIG. 7 is a partial cross-sectional view of embodiment 2 of the thrust cylindrical roller bearing provided by the present invention;
FIG. 8 is a partial cross-sectional view of embodiment 3 of the thrust cylindrical roller bearing provided by the present invention;
FIG. 9 is a partial cross-sectional view of embodiment 4 of the thrust cylindrical roller bearing provided by the present invention;
FIG. 10 is a partial cross-sectional view of embodiment 5 of the thrust cylindrical roller bearing provided by the present invention;
FIG. 11 is an exploded view of embodiment 6 of the thrust cylindrical roller bearing provided by the present invention;
reference numerals: 1-inner ring, 2-outer ring, 3-retainer, 4-cylindrical roller, 5-stopping groove, 6-rolling body, 21-mounting groove, 31-blocking piece, 32-connector, 33-containing cavity and 311-end surface part.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
Referring to fig. 1 and fig. 2, the present embodiment provides a thrust cylindrical roller bearing, which includes an inner ring 1, an outer ring 2, a cage 3, and a plurality of cylindrical rollers 4, wherein:
specifically, referring to fig. 3 and fig. 4, the retainer 3 includes two end surface portions 311 disposed opposite to each other and a plurality of connecting bodies 32 for connecting the two end surface portions 311, the plurality of connecting bodies 32 are disposed along the circumferential direction of the end surface portions 311, and a receiving cavity 33 for receiving the cylindrical roller 4 is formed between adjacent connecting bodies 32, and the main function of the connecting bodies 32 is to separate the cylindrical roller 4, so that it is easy to understand that the cross-sectional shape of the connecting bodies 32 should not be limited, and the cylindrical connecting body 32 is selected in this embodiment. In this embodiment, the retainer 3 is designed in a split manner, and includes two blocking pieces 31, the two blocking pieces 31 are close to each other to form an annular end surface portion 311, and two end surfaces of the cylindrical roller 4 are respectively abutted against the two end surface portions 311.
Further, referring to fig. 5 and 6, at least one of the inner ring 1 and the outer ring 2 is provided with a stop groove 5 at each of two axial ends thereof, which correspond to the two end surface portions 311. At least one of the radial outer side and the radial inner side of one end surface portion 311 is limited by the stop groove 5 to prevent the end surface portion 311 from being separated from the inner ring 1 or the outer ring 2, and at least one of the radial outer side and the radial inner side of the other end surface portion 311 is limited by the stop groove 5 to prevent the end surface portion 311 from being separated from the inner ring 1 or the outer ring 2. When the abutment grooves 5 are formed in the outer ring 2, the abutment grooves 5 are formed on both sides of the inner peripheral surface of the outer ring 2 and are recessed radially outward, and when the abutment grooves 5 are formed in the outer ring 2, the abutment grooves 5 are formed on both sides of the outer peripheral surface of the inner ring 1 and are recessed radially inward.
In order to reduce the friction between the end surface of the cylindrical roller 4 and the baffle 31, the contact surface between the end surface of the cylindrical roller 4 and the baffle 31 should be reduced as much as possible, so that a through hole is formed in the baffle 31 at the contact position with the end surface of the cylindrical roller 4, the diameter of the through hole is smaller than that of the cylindrical roller 4, and the weight of the retainer 3 can be reduced by forming the through hole.
Example 1:
in this embodiment, only the outer ring 2 is provided with the stop groove 5, and the outer diameter of the baffle 31 is larger than the inner peripheral surface diameter of the outer ring 2 and smaller than the annular surface diameter of the stop groove 5, so the end surface portions 311 of the two baffles 31 abut against the stop groove 5, the end surface of the cylindrical roller 4 is pressed by the end surface portions 311 of the two baffles 31, and the connecting body 32 is fixedly connected between the two baffles 31, specifically, the connecting body 32 can be connected in a manner that both ends are riveted with the baffles 31, after riveting, there is a very small gap between the stop groove 5 and the two end surface portions 311 to ensure a certain adjustment clearance of the bearing in the axial direction, the axial clearance is determined by the depth of the stop groove 5 and the length of the connecting body 32, and since riveting may affect the length of the connecting body 32, riveting also affects the axial clearance, therefore, the connecting body 32 should be in a manner of single-side riveting as much as possible, that one end of the, the other end is riveted with another baffle 31 to reduce uncertain factors in the machining process and control the precision of the axial clearance. In addition, there is also a very small gap between the retainer 3 and the circumferential surface of the abutment groove 5 in the radial direction, preventing the retainer 3 from being locked by the abutment groove 5 in the radial direction.
The following describes in detail an assembling process of the thrust cylindrical roller bearing according to this embodiment: firstly, a baffle 31 is arranged in the outer ring 2, then the cylindrical roller 4 is arranged, the connecting body 32 is arranged, the other baffle 31 is arranged on the other side, then the connecting body 32 and the baffle 31 are riveted, and finally the inner ring 1 is arranged.
The working principle of the thrust cylindrical roller bearing provided by the embodiment is described in detail as follows: compared with the NU type cylindrical roller 4 bearing in the prior art, the bearing in the present embodiment has no flange on the outer ring 2, so that it is not necessary to machine an inside relief groove, and the cylindrical roller 4 is axially positioned to abut against the abutting groove 5 by the two end surface portions 311 of the cage 3, and it is easy to understand that only the inner ring 1 of the bearing may abut against the end surface portions 311 by the abutting groove 5, and at this time, the inside diameter of the baffle 31 should be smaller than the diameter of the circumferential surface of the inner ring 1 and larger than the diameter of the circumferential surface of the abutting groove 5 at the inner ring 1.
Example 2:
referring to fig. 7, the embodiment 2 is basically the same as the embodiment 1, and will not be described herein again, except that: the inner ring 1 is provided with the abutting groove 5, and the inner diameter of the end surface portion 311 is larger than the diameter of the circumferential surface of the abutting groove 5 at the inner ring 1 and smaller than the diameter of the circumferential surface at the inner ring 1, so that the abutting groove 5 at the inner ring 1 and the end surface portion 311 of the cage 3 are axially positioned by the cylindrical rollers 4. At this time, the bearing inner ring 1 and the bearing outer ring 2 cannot bear axial load.
Example 3:
referring to fig. 8, embodiment 3 is substantially the same as embodiment 1, and will not be described herein, except that: the inner ring 1 and the outer ring 2 are both provided with a butting groove 5, one end face part 311 is butted with the butting groove 5 at the inner ring 1, and the other end face part 311 is butted with the butting groove 5 at the outer ring 2. At this time, the bearing inner ring 1 and the bearing outer ring 2 can bear axial load respectively in the directions shown by arrows in the figure.
Example 4:
referring to fig. 9, the embodiment 4 is substantially the same as the embodiment 1, and will not be described herein again, except that: the inner ring 1 and the outer ring 2 are both provided with a butting groove 5, one end face part 311 is butted with the butting groove 5 at the inner ring 1, and the other end face part 311 is butted with the outer ring 2 and the butting groove 5 at the inner ring 1. At this time, the bearing inner ring 1 and the bearing outer ring 2 can bear axial load respectively in the directions shown by arrows in the figure.
Example 5:
referring to fig. 10, the embodiment 5 is substantially the same as the embodiment 1, and will not be described herein again, except that: the inner ring 1 and the outer ring 2 are all provided with a butting groove 5, one end face part 311 is all butted with the butting grooves 5 at the inner ring 1 and the outer ring 2, and the other end face part 311 is butted with the butting grooves 5 at the outer ring 2 and the inner ring 1. At this time, the bearing inner ring 1 and the bearing outer ring 2 can bear axial load respectively in the directions shown by arrows in the figure.
Example 6:
referring to fig. 11, embodiment 6 is substantially the same as embodiment 1, and will not be described herein, except that:
the abutting groove 5 is not directly abutted with the end surface portion 311, but the rolling body 6 is clamped, sliding friction is generated when the abutting groove 5 is directly abutted with the end surface portion 311, and rolling friction is generated when the rolling body 6 is clamped, so that the rolling body 6 in the implementation can reduce the friction force generated when the abutting groove 5 and the end surface portion 311 rotate relatively, the abrasion between the abutting groove 5 and the retainer 3 is greatly reduced, the service life is prolonged, and larger axial load can be borne under the condition of ensuring a certain bearing service life.
The rolling elements 6 may be balls, which are selected in the embodiment, or may be rollers, and if the rolling elements are rollers, the rotation axes of the rollers should be in the same plane as the bearing axis.
In addition, in order to prevent the adjacent rolling bodies 6 from colliding and rubbing, the abutting groove 5 needs to be provided with an installation groove 21 matched with the rolling body 6, or the rolling body 6 is limited by a structure similar to the retaining structure of the thrust bearing, which is not described in detail herein.
In summary, according to the thrust cylindrical roller bearing provided by the invention, the inner ring or the outer ring is provided with the abutting groove, and the end surface part of the retainer is abutted against the abutting groove, so that the cylindrical roller is axially limited, and the bearing flange in the prior art is effectively replaced.
The above embodiments of the present invention should not be construed as limiting the scope of the present invention. Any other corresponding changes and modifications made according to the technical idea of the present invention should be included in the protection scope of the claims of the present invention.

Claims (10)

1. The utility model provides a thrust formula cylindrical roller bearing which characterized in that, includes inner circle, outer lane, holder and a plurality of cylindrical roller, wherein:
the retainer comprises two annular end face parts which are oppositely arranged and a plurality of connecting bodies which are connected with the two end face parts, the plurality of connecting bodies are circumferentially arranged along the end face parts, and an accommodating cavity for accommodating the cylindrical roller is formed between the adjacent connecting bodies;
at least one of the inner ring and the outer ring is provided with a stop groove at two axial ends, which correspond to the two end surface parts respectively;
when the inner ring is provided with the stopping grooves, the inner sides of the two end surface parts along the radial direction are respectively abutted against the two stopping grooves;
when the outer ring is provided with the stopping grooves, the outer sides of the two end surface parts along the radial direction are respectively abutted against the two stopping grooves;
when the same sides of the inner ring and the outer ring are both provided with the abutting grooves, the inner sides or the outer sides of the two end surface parts along the radial direction are respectively abutted against any corresponding abutting groove and/or the two abutting grooves on the same side;
and two end faces of the cylindrical roller are respectively abutted against the two end face parts.
2. The thrust cylindrical roller bearing according to claim 1, wherein rolling elements are interposed between the abutting groove and the end surface portion to reduce a frictional force when the abutting groove and the end surface portion rotate relative to each other.
3. The thrust cylindrical roller bearing according to claim 1, wherein the abutting grooves are formed on both sides of the inner peripheral surface of the outer ring and are recessed radially outward.
4. The thrust cylindrical roller bearing according to claim 1, wherein the stopper grooves are formed on both sides of the outer peripheral surface of the inner ring and are recessed radially inward.
5. A thrust cylindrical roller bearing according to claim 3, wherein the end surface portions have a diameter on the outer side in the radial direction larger than the diameter on the inner peripheral surface of the outer ring and smaller than the diameter on the peripheral surface of the abutment groove at the outer ring, and a diameter on the inner side in the radial direction larger than the diameter on the outer peripheral surface of the inner ring.
6. The thrust cylindrical roller bearing according to claim 4, wherein a diameter of an inner side in a radial direction of the end surface portions is smaller than a diameter of an outer peripheral surface of the inner ring and larger than a diameter of a peripheral surface of the abutment groove at the inner ring, and a diameter of an outer side in the radial direction of the end surface portions is smaller than a diameter of the inner peripheral surface of the outer ring.
7. A thrust cylindrical roller bearing according to any one of claims 3 and 4, wherein an outside diameter of one of the end surface portions in the radial direction is larger than an inside diameter of the outer ring in the radial direction and smaller than the diameter of the circumferential surface of the abutment groove at the outer ring, and an inside diameter of the other of the end surface portions in the radial direction is smaller than the diameter of the outer circumferential surface of the inner ring and larger than the diameter of the circumferential surface of the abutment groove at the inner ring.
8. A thrust cylindrical roller bearing according to any one of claims 3 and 4, wherein an outside diameter of one of the end surface portions in the radial direction is larger than an inner peripheral surface diameter of the outer ring and smaller than the abutment groove peripheral surface diameter at the outer ring; the inner diameter of the other end surface part in the radial direction is smaller than the diameter of the outer peripheral surface of the inner ring and larger than the diameter of the peripheral surface of the abutting groove at the inner ring, and the outer diameter of the end surface part in the radial direction is larger than the diameter of the inner peripheral surface of the outer ring and smaller than the diameter of the peripheral surface of the abutting groove at the outer ring.
9. A thrust cylindrical roller bearing according to any one of claims 3 and 4, wherein the end surface portions have a diameter radially outside larger than the diameter of the inner peripheral surface of the outer race and smaller than the diameter of the circumferential surface of the abutment groove at the outer race, and have a diameter radially inside smaller than the diameter of the outer peripheral surface of the inner race and larger than the diameter of the circumferential surface of the abutment groove at the inner race.
10. The thrust cylindrical roller bearing of claim 1, wherein the retainer comprises two blocking pieces, the two blocking pieces are fixedly connected, and the side where the two blocking pieces are close to each other forms the end surface portion.
CN202011034755.5A 2020-09-27 2020-09-27 Thrust type cylindrical roller bearing Pending CN112211901A (en)

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Application Number Priority Date Filing Date Title
CN202011034755.5A CN112211901A (en) 2020-09-27 2020-09-27 Thrust type cylindrical roller bearing

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Application Number Priority Date Filing Date Title
CN202011034755.5A CN112211901A (en) 2020-09-27 2020-09-27 Thrust type cylindrical roller bearing

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Cited By (4)

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Publication number Priority date Publication date Assignee Title
CN112922963A (en) * 2021-03-12 2021-06-08 苏州普瑞川传动科技有限公司 Separated bearing retainer and cylindrical roller bearing
CN113847337A (en) * 2021-08-16 2021-12-28 人本股份有限公司 Ball bearings with large and small ball structures
CN116398465A (en) * 2023-06-07 2023-07-07 江苏万勤风机有限公司 Integrated bearing pedestal for industrial fan
TWI859604B (en) * 2022-10-17 2024-10-21 銀泰科技股份有限公司 Roller bearing and retainer

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CN109931434A (en) * 2017-12-18 2019-06-25 中核苏阀科技实业股份有限公司 A kind of low friction valve rod anti-rotation guide frame

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Publication number Priority date Publication date Assignee Title
JP2010031947A (en) * 2008-07-28 2010-02-12 Nsk Ltd Rolling bearing
JP2012247026A (en) * 2011-05-30 2012-12-13 Ntn Corp Cylindrical roller bearing
CN203009574U (en) * 2012-12-12 2013-06-19 中山市盈科轴承制造有限公司 Cylindrical roller bearing
CN103539021A (en) * 2013-10-31 2014-01-29 王玉文 Tower arm anti-friction device
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112922963A (en) * 2021-03-12 2021-06-08 苏州普瑞川传动科技有限公司 Separated bearing retainer and cylindrical roller bearing
CN113847337A (en) * 2021-08-16 2021-12-28 人本股份有限公司 Ball bearings with large and small ball structures
TWI859604B (en) * 2022-10-17 2024-10-21 銀泰科技股份有限公司 Roller bearing and retainer
CN116398465A (en) * 2023-06-07 2023-07-07 江苏万勤风机有限公司 Integrated bearing pedestal for industrial fan
CN116398465B (en) * 2023-06-07 2023-12-15 江苏万勤风机有限公司 Integrated bearing pedestal for industrial fan

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Application publication date: 20210112