CN105545961B - A low noise deep groove ball bearing - Google Patents
A low noise deep groove ball bearing Download PDFInfo
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- CN105545961B CN105545961B CN201510626493.4A CN201510626493A CN105545961B CN 105545961 B CN105545961 B CN 105545961B CN 201510626493 A CN201510626493 A CN 201510626493A CN 105545961 B CN105545961 B CN 105545961B
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- outer ring
- sealing
- inner ring
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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
- F16C33/3806—Details of interaction of cage and race, e.g. retention, centring
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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
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
- F16C33/7896—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members with two or more discrete sealings arranged in series
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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
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
- F16C19/166—Four-point-contact ball bearings
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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
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
-
- 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
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
- F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
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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
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
- F16C33/7893—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a cage or integral therewith
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
本发明提供一种低噪音的深沟球轴承，所述的轴承外圈和轴承内圈之间的空腔中分布有由两部分相互扣合的轴承保持架(6)，轴承保持架(6)在轴承球(3)之间的结合位置使用榫和凹槽的结合形式，所述轴承保持架(6)在轴承外圈(1)和轴承内圈(2)之间轴向上，球形腔体的两侧部分形成为两个环形的槽(6.2，6.4)，两个槽的开口向轴承球滚道打开并且开口发散。
The invention provides a low-noise deep groove ball bearing, wherein the cavity between the bearing outer ring and the bearing inner ring is distributed with a bearing cage (6) which is mutually engaged by two parts, the bearing cage (6) ) Use a tenon and groove combination form at the joint position between the bearing balls (3), the bearing cage (6) is axially between the bearing outer ring (1) and the bearing inner ring (2), spherical The two side parts of the cavity are formed as two annular grooves (6.2, 6.4), the openings of the two grooves are open to the bearing ball raceway and the openings diverge.
Description
Technical Field
The invention relates to a deep groove ball bearing, in particular to a low-noise deep groove ball bearing.
Background
Deep groove ball bearings are the most common rolling bearings, are suitable for high speed operation, and are durable and maintenance free. The deep groove ball bearing is generally required to have small friction coefficient, high limit rotating speed and low manufacturing cost. The size and the shape of the motor are various, and the motor is suitable for industries such as precision instruments, low-noise motors, automobiles and the like.
The deep groove ball bearing is composed of an inner bearing ring, an outer bearing ring and a plurality of bearing balls arranged between the bearing rings, the bearing balls are arranged in groove-shaped roller paths in the inner surfaces of the inner bearing ring and the outer bearing ring, and the deep groove ball bearing is difficult to be fully lubricated due to the fact that the annular roller paths of the inner ring and the outer ring of the deep groove ball bearing are closed with the balls. The sealing rings are arranged at two ends or one end of the bearing to prevent the grease filled in advance from leaking, but the bearing can be filled once when being delivered from a factory, and has the defects of solidification and agglomeration of the grease, difficulty in replacement and the like after being used for a long time.
Meanwhile, the bearing needs to adopt the sealing cover due to the sealing requirement, but the sealing cover is not reliably riveted due to the heat treatment deformation of the outer ring tooth socket, and the cover falling phenomenon often occurs in the bearing moving process. As in german patent DE4214655a1, providing a sealing cap on a deep groove ball bearing and then overlapping the inner and outer bearing rings results in an increase in the volume of the circumferential cavity, but the sealing cap is prone to wear in use, so that grease leakage occurs.
In addition, the single-row deep groove ball bearing is a rigid radial rolling bearing, the radial axial bearing capacity is required to be the same, and the friction is small, so that the bearing can bear high rotating speed. As in DE168499a1, the two bearing rings are arranged eccentrically to one another and are filled with balls. However, the bearing capacity is limited due to the small bearing balls.
As in japanese patent publication 2002-. However, when the circumferential width of the bearing inner groove is large, the center position of the retainer is largely displaced, and the retainer may be abnormally vibrated during the operation of the bearing, thereby causing interference between the cavity of the retainer and the bearing ball and noise between the retainer and the retainer.
At present, the requirements for noise, life and bearing of the bearings used in the motors are higher and higher, so that research on the structure of the bearings is needed to provide a low-noise deep groove ball bearing.
Disclosure of Invention
In order to overcome the defects in the prior art, the invention aims to provide a low-noise deep groove ball bearing, so that the bearing has the advantages of good silencing effect, easiness in manufacturing, higher bearing capacity and long service life.
The invention provides a low-noise deep groove ball bearing, which comprises a bearing outer ring and a bearing inner ring which is coaxially arranged in the bearing outer ring with the bearing outer ring, wherein a plurality of bearing balls are arranged between the bearing outer ring and the bearing inner ring, and the bearing balls roll in an outer ring raceway on the inner surface of the bearing outer ring and an outer ring raceway on the outer surface of the bearing inner ring; the inner chamber between bearing inner race and the bearing inner race is sealed by two annular seal ring that set up face to face each other axially, fills its characterized in that with bearing lubricant in the inner chamber between bearing inner race and the bearing outer race:
a bearing retainer which is formed by mutually buckling two parts is distributed in a cavity between the bearing outer ring and the bearing inner ring, and the joint position of the bearing retainer between bearing balls adopts a tenon and groove joint mode;
the half edge of the bearing retainer, which is positioned at one side of the bearing ball, comprises a partially spherical cavity, and the two half edge parts form a spherical cavity for containing and retaining the bearing ball;
the bearing retainer is axially arranged between the bearing outer ring and the bearing inner ring, two side parts of the spherical cavity are formed into two annular grooves, and openings of the two grooves are opened towards the bearing ball raceway and are diverged.
Preferably, each side half of the bearing cage has two circumferential ridges at the locations where the bearing cage contacts the bearing outer race and the bearing inner race.
Further, the invention aims to provide a deep groove ball bearing with low noise, and the bearing has a good dustproof effect, and the dustproof cover is not easy to fall off in the using process.
The annular cross-section of the seal ring has a multilayer structure comprising: the radial sealing edge of the outermost layer is inserted into and fixed on the dustproof cover in the radial sealing edge slot of the sealing ring, and the axial sealing lip is attached to the dustproof cover;
the axial sealing lip is provided with a trapezoidal outline with the tail end protruding towards an inner cavity between the bearing outer ring and the bearing inner ring;
the sealing ring on at least one side is located the bearing inner race alveolus, and outer lane alveolus and sealing ring outer lip axial interference fit exist radial clearance simultaneously between the sealing ring and the bearing inner race of this side, and the bearing inner race of this side has the width that subtracts the thickness of sealing ring in the axial direction than the bearing outer lane.
Preferably, the bearing inner ring has a width on one side of the seal ring, which is smaller than the width of the bearing outer ring by the thickness of the seal ring in the axial direction.
Preferably, the inner surface of the bearing inner ring is in scraping contact with a sealing lip formed at the tail end of the radial sealing edge of the sealing ring, and a circumferential inverted tooth groove is formed on the inner surface of the bearing inner ring and matched with a tooth part and a concave part formed by the sealing lip.
The invention has the following beneficial effects:
1. the half-cage on each side has two circumferential ridges at the locations where the bearing cage contacts the bearing outer race and the bearing inner race. On one hand, the ridge part has a labyrinth sealing effect on a closed space between the bearing outer ring and the bearing inner ring; in the second aspect, the structure provides certain flexibility for the edge of the bearing retainer, so that the bearing retainer is easier to be installed in the bearing inner ring and the bearing outer ring in a matching way; in the third aspect, the bearing inner ring and the bearing outer ring which are arranged in a matched manner are provided with the concave parts, and when the bearing rotates, a discontinuous cloth distribution surface on the centrifugal force is formed, so that the lubricant is difficult to diffuse out easily; in the fourth aspect, the central position of the retainer is limited through the matching action of the ridge part and the concave part, the abnormal vibration of the retainer in the bearing operation process is avoided, and the noise generated by the vibration due to the deviation of the central position of the retainer is obviously reduced.
2. The bearing retainer is in the form of a buckling piece at the joint position between the bearing balls, and preferably adopts the combination form of a tenon and a groove, so that two half sides of the bearing retainer are buckled without arranging other connection modes.
3. The axial sealing lip has a trapezoidal profile with the end projecting into the cavity between the bearing outer race and the bearing inner race, the trapezoidal profile helping to prevent lubricant substances from entering directly into the radial gap existing between the sealing ring and the bearing outer race or the bearing inner race when the bearing rotates.
4. The inner surface of the bearing inner ring is provided with the annular inverted tooth groove, on one hand, the inner surface of the inverted tooth groove and the surface of the tooth protruding part form a chamfer, the contact surface between the sealing lip and the bearing inner ring is reduced, on the other hand, the multi-linear sealing surface is formed, the sealing effect of the sealing ring is improved, meanwhile, the shape of the inverted tooth groove is beneficial to forming a fit with the tooth part and the concave part formed by the sealing lip, and the dust cover is prevented from falling off in operation.
5. The bearing retainer is formed into two annular grooves at two side parts of the spherical cavity, the openings of the two grooves are opened to the bearing ball race and are diverged, the two grooves can be symmetrical or asymmetrical, the annular grooves can be used as extra grooves for storing lubricant, the lubricant is temporarily accumulated and prevented from being diffused outwards the bearing retainer during the operation of the bearing, and the lubricant is further redistributed to the ball race through the diverged openings.
Drawings
FIG. 1 is an enlarged cross-sectional view of a deep groove ball bearing of the present invention.
FIG. 2 is an enlarged cross-sectional view of the outer race of the deep groove ball bearing of the present invention.
FIG. 3 is an enlarged cross-sectional view of the inner race of the deep groove ball bearing of the present invention.
FIG. 4 is an enlarged gasket view of the deep groove ball bearing of the present invention.
FIG. 5 is an enlarged cross-sectional view of the cage of the deep groove ball bearing of the present invention.
FIG. 6 is a partial schematic view of an enlarged cage fastener for a deep groove ball bearing of the present invention.
Detailed Description
The present invention is further illustrated by the following examples, which are not intended to limit the invention to these embodiments. It will be appreciated by those skilled in the art that the present invention encompasses all alternatives, modifications and equivalents as may be included within the scope of the claims.
Example 1
The invention provides a low-noise deep groove ball bearing, which comprises a bearing outer ring 1 and a bearing inner ring 2 coaxially arranged with the bearing outer ring in the bearing outer ring as shown in figure 1, wherein a plurality of bearing balls 3 are arranged between the bearing outer ring 1 and the bearing inner ring 2, and the bearing balls 3 can roll in an outer ring raceway on the inner surface of the bearing outer ring 1 and an outer ring raceway on the outer surface of the bearing inner ring 2.
The inner space between the outer bearing ring 1 and the inner bearing ring 2 of the deep groove ball bearing is sealed by two annular sealing rings 5 arranged axially opposite one another, while the inner space between the outer bearing ring 1 and the inner bearing ring 2 is filled with a bearing lubricant.
As shown in fig. 4, the ring-shaped cross section of the seal ring 5 has a multi-layer structure, including an outermost radial sealing edge 5.4, a dust cap 5.5 inserted and fixed in a slot of the radial sealing edge 5.4 of the seal ring 5, and an axial sealing lip 5.6 attached to the dust cap.
The axial sealing lip has a trapezoidal profile with the ends protruding towards the inner cavity between the bearing outer ring 1 and the bearing inner ring 2, which helps to prevent lubricant substances from entering directly into the radial gap existing between the sealing ring 5 and the bearing outer ring 1 or the bearing inner ring 2 when the bearing is rotating.
As shown in fig. 1 to 4, the seal ring 5 on one side is located in the tooth groove 1.8 of the bearing outer ring 1, the outer ring tooth groove 1.8 is in axial interference fit with the seal ring outer lip 5.1, and a radial gap is present between the seal ring 5 on the one side and the bearing inner ring 2, and the bearing inner ring 2 on the one side has a width of the thickness of the seal ring 5 subtracted in the axial direction from the bearing outer ring 1.
The inner surface of the bearing inner ring 2 keeps scraping contact with a sealing lip 5.8 formed at the tail end of a radial sealing edge 5.4 of the sealing ring 5, a surrounding type inverted tooth groove 2.3 is formed on the inner surface of the bearing inner ring 2, on one hand, a chamfer is formed on the inner surface 2.1 of the inverted tooth groove 2.3 and the surface of a tooth protruding part 2.2, the contact surface of the sealing lip 5.8 and the bearing inner ring 2 is reduced, on the other hand, a multi-linear sealing surface is formed, the sealing effect of the sealing ring is improved, meanwhile, the shape of the inverted tooth groove is beneficial to forming matching with a tooth part 5.3 and a concave part 5.7 formed by the sealing lip 5.8, and the dust cap is prevented from.
Further preferably, a lubricant storage groove surrounding the circumferential direction can be arranged in the raceways of the bearing outer ring 1 and the bearing inner ring 2 to contain more lubricant and prolong the service life of the bearing.
The opposite sealing ring 5 on the other side is positioned in a tooth groove 2.8 of the bearing inner ring 2, the tooth groove 2.8 of the inner ring is in axial interference fit with an outer lip 5.1 of the sealing ring, meanwhile, a radial gap exists between the sealing ring 5 on the side and the bearing outer ring 1, and the bearing outer ring 1 on the side has a width which is obtained by subtracting the thickness of the sealing ring 5 in the axial direction compared with the bearing inner ring 2.
The outer surface of the bearing outer ring 1 keeps scraping contact with a seal lip 5.8 formed at the tail end of a radial seal edge 5.4 of the seal ring 5, a surrounding type inverted tooth groove 1.3 is formed on the outer surface of the bearing outer ring 1, the shape of the inverted tooth groove is beneficial to forming matching with a tooth part 5.3 and a concave part 5.7 formed by the seal lip 5.8, and the dust cover is prevented from falling off in operation.
The present embodiment describes a manner in which the bearings and the seal rings on both sides are asymmetrically configured, but the present invention does not exclude a manner in which the bearings and the seal rings on both sides are symmetrically configured, that is, the bearings and the seal rings may be configured symmetrically about the center of the bearing ball.
Example 2
Further preferably, a bearing retainer 6 which is formed by mutually buckling two parts is distributed in a cavity between the bearing outer ring 1 and the bearing inner ring 2 of the deep groove ball bearing, so that a plurality of bearing balls 3 are distributed and maintained at uniform intervals in the circumferential direction.
As shown in fig. 5, the half of the bearing cage 6 on the side of the bearing ball 3 includes a partially spherical cavity 6.7, the two half portions are formed as spherical cavities for accommodating and holding the bearing ball, and both side portions of the spherical cavities are formed as two annular grooves 6.2 and 6.4 in the axial direction between the bearing outer race 1 and the bearing inner race 2, the openings of the two grooves are open to and divergent from the bearing ball raceway, the two grooves may be symmetrical or asymmetrical, and the annular groove may serve as an additional groove for storing lubricant, temporarily accumulating the lubricant during the bearing operation and preventing it from being dispersed to the outside of the bearing cage, and further redistributing the lubricant to the ball raceway through the divergent openings.
At the location where the bearing cage 6 is in contact with the bearing inner ring 2 and the bearing outer ring 1, the half-cage on each side has two circumferential ridges 6.1 and 6.3. On one hand, the ridge part generates a labyrinth sealing effect on a closed space between the bearing outer ring 1 and the bearing inner ring 2; in the second aspect, the structure provides certain flexibility for the edge of the bearing retainer, so that the bearing retainer is easier to be installed in the bearing inner ring and the bearing outer ring in a matching way; in the third aspect, when the bearing rotates, the bearing inner ring 2 and the bearing outer ring 1 are matched with the ridge to be installed, and the concave parts 1.5, 1.9 and 2.5, 2.9 on the bearing outer ring 1 form a discontinuous cloth distribution surface on centrifugal force, so that the lubricant is difficult to diffuse out easily; in the fourth aspect, the central position of the retainer is limited through the matching action of the ridge part and the concave part, the abnormal vibration of the retainer in the bearing operation process is avoided, and the noise generated by the vibration due to the deviation of the central position of the retainer is obviously reduced.
Example 3
Further preferably, as shown in fig. 6, the bearing retainer 6 is formed by using a snap-fit component at the joint position between the bearing balls 3, preferably a tongue-and-groove joint, and the two half sides of the bearing retainer are buckled without providing other connection means.
A further preferred tongue and groove is selected in the shape of a hollow truncated cone with a hole and this hole communicates the bearing cage with the central annular spaces 6.5 and 6.6 of the outer side so that the space between the cages is in fluid communication with the space between the outer and inner rings of the bearing.
The cage and the radial sealing edge can be made of plastic materials, such as polyamide 66 and polyhexamethylene amide, which have good wear resistance under high load, small friction coefficient and good aging resistance. But may of course also be made of conventional materials such as steel.
It will be appreciated by persons skilled in the art that the embodiments of the invention described above and shown in the drawings are given by way of example only and are not limiting of the invention. The functional and structural principles of the present invention may be modified at will without departing from the principles set forth above.
Claims (1)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510626493.4A CN105545961B (en) | 2015-09-24 | 2015-09-24 | A low noise deep groove ball bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510626493.4A CN105545961B (en) | 2015-09-24 | 2015-09-24 | A low noise deep groove ball bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105545961A CN105545961A (en) | 2016-05-04 |
| CN105545961B true CN105545961B (en) | 2020-05-29 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201510626493.4A Active CN105545961B (en) | 2015-09-24 | 2015-09-24 | A low noise deep groove ball bearing |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106122267A (en) * | 2016-06-27 | 2016-11-16 | 芜湖市海联机械设备有限公司 | A kind of linear bearing |
| CN106151282A (en) * | 2016-08-17 | 2016-11-23 | 常州市武进长江滚针轴承有限公司 | Mute type needle bearing |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201359018Y (en) * | 2009-01-15 | 2009-12-09 | 浙江进发轴承有限公司 | Retaining bracket of deep groove ball bearing |
| CN201359009Y (en) * | 2009-01-15 | 2009-12-09 | 浙江进发轴承有限公司 | Deep groove ball bearing |
| JP2011080506A (en) * | 2009-10-05 | 2011-04-21 | Ntn Corp | Deep groove ball bearing and gear supporting device |
| CN102472325A (en) * | 2009-07-25 | 2012-05-23 | 谢夫勒科技有限两合公司 | Rolling bearing, particularly single-row deep groove ball bearing for a dual mass flywheel in a motor vehicle |
| CN203009594U (en) * | 2012-12-12 | 2013-06-19 | 宁波达尔轴承有限公司 | High-speed servo motor bearing |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| IT1404769B1 (en) * | 2010-12-21 | 2013-11-29 | Skf Ab | RESTING BALL CAGE FOR BEARINGS AND RIGID BEARING UNIT |
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2015
- 2015-09-24 CN CN201510626493.4A patent/CN105545961B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201359018Y (en) * | 2009-01-15 | 2009-12-09 | 浙江进发轴承有限公司 | Retaining bracket of deep groove ball bearing |
| CN201359009Y (en) * | 2009-01-15 | 2009-12-09 | 浙江进发轴承有限公司 | Deep groove ball bearing |
| CN102472325A (en) * | 2009-07-25 | 2012-05-23 | 谢夫勒科技有限两合公司 | Rolling bearing, particularly single-row deep groove ball bearing for a dual mass flywheel in a motor vehicle |
| JP2011080506A (en) * | 2009-10-05 | 2011-04-21 | Ntn Corp | Deep groove ball bearing and gear supporting device |
| CN203009594U (en) * | 2012-12-12 | 2013-06-19 | 宁波达尔轴承有限公司 | High-speed servo motor bearing |
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| CN105545961A (en) | 2016-05-04 |
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Address after: 315324 Zhejiang Province Ningbo City Cixi City Zhouxiang Town Xiangtong Road 95-99.NO Patentee after: NINGBO WANFENG BEARING Co.,Ltd. Country or region after: China Address before: 315324 Zhejiang Province Cixi City Zhouxiang Town Zhouxi Road 328 No. Patentee before: NINGBO WANFENG BEARING Co.,Ltd. Country or region before: China |
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