CN106168255A - Taper roller formula eliminates the protection bearing arrangement of rotor footpath axial gap simultaneously - Google Patents
Taper roller formula eliminates the protection bearing arrangement of rotor footpath axial gap simultaneously Download PDFInfo
- Publication number
- CN106168255A CN106168255A CN201610142213.7A CN201610142213A CN106168255A CN 106168255 A CN106168255 A CN 106168255A CN 201610142213 A CN201610142213 A CN 201610142213A CN 106168255 A CN106168255 A CN 106168255A
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- bearing
- rotor
- tapered roller
- radial
- wedge
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- 238000005096 rolling process Methods 0.000 claims abstract description 38
- 210000004907 gland Anatomy 0.000 claims abstract description 15
- 230000001681 protective effect Effects 0.000 claims description 30
- 238000005520 cutting process Methods 0.000 claims description 4
- 238000006073 displacement reaction Methods 0.000 claims description 3
- 238000000034 method Methods 0.000 claims description 3
- ZZUFCTLCJUWOSV-UHFFFAOYSA-N furosemide Chemical compound C1=C(Cl)C(S(=O)(=O)N)=CC(C(O)=O)=C1NCC1=CC=CO1 ZZUFCTLCJUWOSV-UHFFFAOYSA-N 0.000 claims 1
- 238000005339 levitation Methods 0.000 abstract 1
- 239000000725 suspension Substances 0.000 description 16
- 230000002093 peripheral effect Effects 0.000 description 3
- 229920000049 Carbon (fiber) Polymers 0.000 description 2
- 239000004917 carbon fiber Substances 0.000 description 2
- 239000002131 composite material Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000003365 glass fiber Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000007547 defect Effects 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Classifications
-
- 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
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
- F16C25/08—Ball or roller bearings self-adjusting
-
- 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
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
The invention discloses a kind of taper roller formula and eliminate the protection bearing arrangement of rotor footpath axial gap simultaneously, including rotor, protection bearing, bearing gland, screw and bearing block.Rotor tip is processed into tapered inclined-plane；Wedge shape plectane, for two pieces, left and right, it is axially located at the outside of circular connector, it is installed on rolling bearing inner ring in an interference fit, wedge shape plectane inner circumferential surface configuration is the repetition arc section corresponding with taper roller number, and each arc section is gradually reduced to two ends by centre with the radial distance L2 at device center；Location cylinder is installed on rolling bearing inner ring；Taper roller is oppositely positioned with rotor bevel direction；Roller Shaft outer round surface contacts with wedge shape plectane inner surface.The present invention enough eliminates the radial and axial gap between rotor and taper roller, eliminate the radial and axial gap between rotor and rolling bearing, eliminate vibration and impact to rolling bearing after high speed rotor falls, meet the needs of high-speed magnetic levitation bearing arrangement development.
Description
Technical Field
The invention relates to the technical field of magnetic suspension bearing systems, in particular to a conical roller type protective bearing device for simultaneously eliminating radial and axial gaps of a rotor.
Background
In a magnetic suspension bearing system, a set of protective bearings (also called auxiliary bearings, backup bearings, holding bearings or emergency bearings) are generally required to serve as temporary supports in emergency situations such as system power failure, overload, control system failure or malfunction. The conical roller type centripetal thrust protection bearing capable of automatically eliminating the rotor clearance can bear loads in the radial direction and the axial direction at the same time, and the rotor rotating at a high speed is prevented from colliding and rubbing with a stator part of a system, so that the safety and the reliability of the whole system are guaranteed. The conventional protective bearing design is to assemble a rolling bearing in a bearing seat, and the radial/axial clearance required by the normal operation of a magnetic suspension bearing arranged between an inner ring of the rolling bearing and a rotor is generally half of the radial clearance between the rotor and the radial/axial magnetic suspension bearing. Therefore, the protective bearing is greatly impacted and vibrated when working, and simultaneously, because the rotor can not eliminate the clearance between the protective bearing and the rotor after falling, the protective bearing has poor impact and vibration resistance, and is easy to be damaged, thereby causing serious accidents of the damage of the magnetic suspension bearing system. Therefore, protecting the bearing has been a major factor that restricts the application and development of magnetic bearing systems.
Because the rotating speed of the magnetic suspension bearing system is generally high, and a large radial gap exists between the rotor and the protective bearing, the rotor can generate large impact and vibration when falling onto the protective bearing. At present, a method is that rolling bearings are fully distributed in the circumferential direction of a rotor assembly, and after the rotor assembly falls, gaps are eliminated through the movement of peripheral rolling bearings, but the structure of the method is very complex, only radial gaps can be eliminated, axial gaps cannot be eliminated, and the diameter of a rotor is far larger than that of peripheral rolling bearings, so that the rotating speed of the peripheral rolling bearings is far larger than the limit rotating speed of the rotor after the rotor falls, and the problem is not solved fundamentally.
At present, a protective bearing device capable of completely eliminating radial and axial clearances of a rotor at the same time is not available.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention provides a conical roller type protective bearing device which can simultaneously eliminate radial and axial clearances of a rotor.
The technical scheme adopted by the invention for solving the technical problems is as follows: a taper roller type protective bearing device for simultaneously eliminating radial and axial clearances of a rotor comprises the rotor, a radial protective bearing, a bearing gland, a screw and a bearing seat, wherein the bearing gland is fixedly connected with the bearing seat through the screw, the radial protective bearing is axially compressed, and the bearing seat is fixedly connected with an external machine base;
the radial protection bearing comprises a tapered roller, an annular connecting piece, an elastic supporting piece, a guide groove, a wedge-shaped circular plate, a positioning cylinder and a rolling bearing;
the annular connecting piece is internally and uniformly provided with guide grooves corresponding to the number of the tapered rollers along the circumferential direction;
the elastic supporting piece is arranged between each guide groove in the annular connecting piece and the tapered roller shaft and can allow the radial displacement of the tapered roller;
the outer ring of the rolling bearing is arranged in the bearing seat and is axially compressed through the bearing gland;
the end part of the rotor is processed into an inclined plane with conicity;
the wedge-shaped circular plates are divided into a left circular plate and a right circular plate, are axially arranged on the outer side of the annular connecting piece and are arranged on the inner ring of the rolling bearing in an interference fit mode, repeated arc sections corresponding to the number of the tapered rollers are arranged on the inner circumferential surface of each wedge-shaped circular plate, and the radial distance L2 between each arc section and the center of the device is gradually reduced from the middle to the two ends;
the positioning cylinder is arranged at the axial middle position of the two wedge-shaped circular plates, is arranged on the inner ring of the rolling bearing in an interference fit manner in accordance with the wedge-shaped circular plates, and has a width slightly larger than that of the annular connecting piece;
the taper of the tapered roller is the same as that of the end part of the rotor, but the tapered roller is arranged in the direction opposite to the direction of the inclined plane of the rotor, and a gap L1 with uniform size exists between the tapered roller and the surface of the end part of the rotor along the axial direction; in addition, the tapered roller comprises more than 2 tapered roller split bodies, and each tapered roller split body is distributed in a guide groove arranged in the annular connecting piece through roller shafts arranged at two ends; meanwhile, the outer circle surface of the roller shaft is in contact with the inner surface of the wedge-shaped circular plate.
According to another embodiment of the present invention, it further comprises that the number of the tapered roller split bodies is 2 to 200.
According to another embodiment of the present invention, it is further included that the rolling bearing is a deep groove ball bearing, or a pair of angular contact bearings.
According to another embodiment of the present invention, the elastic supporting member is a separate spring element or a structure integrated with the annular connecting member and processed by wire cutting or the like.
According to another embodiment of the invention, the bearing gland is disc-shaped, the disc is provided with a circle of screw holes along the circumference, and the bearing gland is pressed at the joint of the bearing seat and the rolling bearing.
According to another embodiment of the present invention, it is further included that the radial protection bearing material is a composite material made of metal or carbon fiber/glass fiber.
The invention has the advantages that the invention can simultaneously provide radial and axial protection for the aligned/reversed rotor after the magnetic suspension bearing system fails, and can eliminate the radial and axial gaps between the rotor and the tapered roller, namely eliminate the radial and axial gaps between the rotor and the rolling bearing, thereby eliminating the vibration and impact on the rolling bearing after the high-speed rotor falls down, improving the reliability and safety of the centripetal thrust protection bearing, and meeting the development requirement of the high-speed magnetic suspension bearing system.
Drawings
The invention is further illustrated with reference to the following figures and examples.
Fig. 1 is a schematic structural diagram of a tapered roller type protective bearing device for simultaneously eliminating radial and axial clearances of a rotor according to the invention.
Fig. 2 is a cross-sectional view a-a at the rotor in fig. 1.
Fig. 3 is an enlarged view of a portion I of fig. 2.
In the figure, the rotor comprises a rotor 1, a rotor 2, an annular connecting piece 3, an elastic supporting piece 4, a guide groove 5, a tapered roller 51, a tapered roller split body 52, a roller shaft 6, a wedge-shaped circular plate 7, a positioning cylinder 8, a rolling bearing 9, a bearing gland 10, a screw 11 and a bearing seat.
Detailed Description
The attached drawings disclose a schematic structural diagram of a preferred embodiment of the invention without limitation; the technical solution of the present invention will be described in detail below with reference to the accompanying drawings.
As shown in fig. 1 to 3, a tapered roller type protective bearing device for simultaneously eliminating radial and axial clearances of a rotor includes a rotor 1, a radial protective bearing, a bearing gland 9, a screw 10 and a bearing seat 11, wherein the bearing gland 9 is fixedly connected with the bearing seat 11 through the screw 10, the radial protective bearing is axially compressed, and the bearing seat 11 is fixedly connected with an external machine base. Specifically, the bearing cover 9 is disc-shaped, and the bearing cover 9 is pressed at a joint between the bearing seat 11 and the rolling bearing 9.
The radial protection bearing includes a tapered roller 5, an annular connecting member 2, an elastic support member 3, a guide groove 4, a wedge disk 6, a positioning cylinder 7, and a rolling bearing 8. All radial protective bearing materials are metal or composite materials made of carbon fiber/glass fiber.
Wherein,
the annular connecting piece 2 is provided with guide grooves 4 corresponding to the number of the tapered rollers 5 along the circumferential direction.
The elastic support member 3, which is provided between each guide groove 4 in the annular link member 2 and the tapered roller shaft 5, allows radial displacement of the tapered roller shaft 5. The elastic support member 8 is an independent spring element or a structure which is integrated with the annular connecting member and is processed by a wire cutting process or the like.
The rolling bearing 8 and the outer ring of the rolling bearing 8 are arranged in the bearing seat 11 and are axially pressed through the bearing gland 9. The rolling bearing 8 is a deep groove ball bearing or a pair of angular contact bearings.
The end of the rotor 1 and the end of the rotor 1 are processed into a taper inclined plane.
The wedge-shaped circular plate 6 is divided into a left circular plate and a right circular plate, is axially arranged on the outer side of the annular connecting piece 6 and is arranged on the inner ring of the rolling bearing 8 in an interference fit mode, repeated circular arc sections H1 corresponding to the number of the tapered rollers 5 are arranged on the inner circumferential surface of the wedge-shaped circular plate 6, and the radial distance L2 between each circular arc section and the center of the device is gradually reduced from the middle to two ends.
And the positioning cylinder 7 is arranged at the axial middle position of the two wedge-shaped circular plates, is arranged on the inner ring of the rolling bearing 8 in an interference fit manner in accordance with the wedge-shaped circular plates, and the width of the positioning cylinder 7 is slightly larger than that of the annular connecting piece 2.
The taper of the tapered roller 5 is the same as that of the end part of the rotor, but the tapered roller 5 is arranged in the direction opposite to the inclined plane of the rotor 1, and a gap L1 with uniform size exists between the tapered roller 5 and the end surface of the rotor 1 along the axial direction; in addition, the tapered roller 5 comprises more than 2 tapered roller split bodies 51, and each tapered roller split body 51 is distributed in the guide groove 4 arranged in the annular connecting piece 2 through the roller shafts 52 arranged at two ends; meanwhile, the outer circumferential surface of the roller shaft 52 is in contact with the inner surface of the wedge disk 6. The number of the tapered roller split bodies 51 is 2-200.
When the magnetic suspension bearing normally works, the annular connecting piece 2 and the elastic supporting piece 3 enable all the tapered rollers 5 to be separated and positioned at the middle position of the arc section of the inner surface of the wedge-shaped circular plate 6 at any moment, namely the separation position A of the tapered rollers 5 shown in the figure 2; uniform gaps exist between the split inner circles of all the tapered rollers 5 and the end inclined planes of the rotor 1, so that the bearing device is protected and normal rotation of the rotor 1 is not disturbed. In order to make the clearances between all the tapered roller 5 segments and the rotor 1 uniform, it is necessary to ensure that the tapered roller 5 segments are concentrically arranged with the rotor 1, that is, the center positions of the rolling bearing 8, the wedge disk 6, the tapered rollers 5, and the rotor 1 are aligned with each other.
In addition, in this embodiment, the annular connecting member is an annular connecting rod, and the elastic supporting member is a spring or an elastic body formed by a warp cutting process and the like integrally with the annular connecting member.
When the magnetic suspension bearing system works normally, the radial clearance between the inner circle surface of the tapered roller 5 and the rotor 1 is about 0.15 mm, the inner circle surface and the rotor 1 are not in contact with each other, the rotor 1 rotates at a high speed, and the tapered roller 5 and the inner ring of the rolling bearing 8 are in a static state; when the magnetic suspension bearing fails, the rotor 1 falls, the end part of the rotor 1 is contacted and collided with part of the conical rollers 5 in a split manner, the friction force generated between the conical rollers 5 in the split manner and the rotor 1 drives the roller shafts at two ends of the conical rollers 5 in the inner circumferential surface of the wedge-shaped circular plate 6 to roll relatively along the rotation direction of the rotor, and as all the conical rollers 5 in the split manner are connected through the annular connecting piece 2, as long as one conical roller 5 in the split manner rolls relatively with the wedge-shaped circular plate 6, the roller shafts of other conical rollers 5 in the split manner inevitably roll relatively at the same time; since the inner surface of the arc segment in the wedge-shaped circular plate 6 is arranged to be gradually reduced from the middle to the two ends in the radial distance from the center of the device, therefore, after the tapered roller 5 sub-bodies collide with the rotor 1, all the tapered roller 5 sub-bodies move in the radial direction close to the center of the device, and the movement causes the clearance between all the tapered roller 5 sub-bodies and the rotor 1 to be rapidly reduced, when all the conical roller 5 split bodies roll from the position A to the position B relative to the arc section on the inner surface of the wedge-shaped circular plate 6, the clearance between the conical roller 5 split bodies and the rotor 1 is reduced to zero, so that the gaps between the rotor 1 and all the split bodies of the tapered rollers 5 are eliminated, and since the end parts of the rotor 1 and the tapered rollers 5 have the same taper and are oppositely arranged, therefore, when the clearance between the rotor 1 and all the tapered rollers 5 is eliminated to zero, it is equivalent to simultaneously eliminate the radial and axial clearances between the rotor 1 and the inner ring of the rolling bearing 8. Therefore, the impact and vibration to the protective bearing after the rotor falls off are eliminated, the service life of the centripetal thrust protective bearing in the magnetic suspension bearing system can be obviously prolonged, and the device can play a role in simultaneously protecting the rotor from falling off along the clockwise direction or the anticlockwise direction.
The working principle of the invention is as follows:
when mounting, the tapered roller 5 sub-bodies are brought to the initial positions (positions a) of the inner surfaces of the wedge disks 6 by the elastic supports 3 acting on the tapered roller 5 sub-bodies, and each of the tapered roller 5 sub-bodies is brought to such an initial position by the action of the annular link 2. When the magnetic suspension bearing system normally operates, all the conical roller 5 split bodies are always at initial positions and are in a static state together with the wedge-shaped circular plate 6, the annular connecting piece 2, the elastic supporting piece 3 and the inner ring of the rolling bearing 8, and at the moment, a normal protection gap (generally about 0.15 mm) of the magnetic suspension bearing system exists between the conical inclined plane at the end part of the rotor 1 and the conical inclined plane of each conical roller 5 split body. When the magnetic suspension bearing system fails, the rotor 1 falls down to collide and contact with the partial conical roller 5 split bodies, at this time, on one hand, a large relative speed exists between the rotor 1 and the conical roller 5, on the other hand, a collision force acts, friction force generated by the collision force between the rotor 1 and the conical roller 5 enables the roller shafts of the partial conical roller 5 split bodies to roll relatively on the inner surface of the wedge-shaped circular plate 6 along the rotation direction of the rotor 1, and through the action of the annular connecting piece 2, the roller shafts of other conical roller 5 split bodies can also roll relatively to the wedge-shaped circular plate 6. Because the inner circumferential surface of the wedge-shaped circular plate 6 is provided with repeated circular arc sections corresponding to the number of the tapered rollers 5, and the radial distance between each circular arc section and the center of the device is gradually reduced from the middle to two ends, after the rotor 1 collides with the tapered rollers 5, all the tapered rollers 5 move close to the center of the device in the radial direction, when the radial distance and the protective gap of the tapered rollers 5 rolling along the inner circumferential surface of the wedge-shaped circular plate 6 are equal to each other (the tapered rollers 5 roll to the opposite position B), that is, the gap between the rotor 1 and the tapered rollers 5 is completely eliminated, which is equivalent to simultaneously eliminating the radial and axial gaps existing between the rotor 1 and the rolling bearing 8. At this time, all the tapered rollers 5, the annular connecting piece 2 and the rolling bearings 8 rotate together with the rotor 1 around the rotation center of the magnetic suspension bearing system during normal operation, so that collision between the rotor and the protection bearing is avoided, repeated impact and vibration on the protection bearing are avoided, and the service life of the protection bearing is prolonged.
Claims (5)
1. A conical roller type protective bearing device capable of eliminating radial and axial gaps of a rotor at the same time comprises the rotor (1), a protective bearing, a bearing gland (9), a screw (10) and a bearing seat (11), wherein the bearing gland (9) is fixedly connected with the bearing seat (11) through the screw (10), the protective bearing is axially compressed, and the bearing seat (11) is fixedly connected with an external machine base;
the protective bearing comprises a tapered roller (5), an annular connecting piece (2), an elastic supporting piece (3), a guide groove (4), a wedge-shaped circular plate (6), a positioning cylinder (7) and a rolling bearing (8);
the annular connecting piece (2) is internally and uniformly provided with guide grooves (4) corresponding to the number of the tapered rollers (5) along the circumferential direction;
the elastic supporting piece (3) is arranged between each guide groove (4) in the annular connecting piece (2) and the tapered roller shaft (52) and can allow the radial displacement of the tapered roller (5);
the outer ring of the rolling bearing (8) is arranged in the bearing seat (11) and is axially compressed through the bearing gland (9);
it is characterized in that the utility model is characterized in that,
the end of the rotor (1) is processed into a tapered inclined plane;
the wedge-shaped circular plates (6) are arranged on the left and right sides, are axially arranged on the outer side of the annular connecting piece (2), and are arranged on the inner ring of the rolling bearing (8) in an interference fit manner, repeated arc sections H1 corresponding to the number of the tapered rollers (5) are arranged on the inner circumferential surface of each wedge-shaped circular plate (6), and the radial distance L2 between each arc section and the center of the device is gradually reduced from the middle to the two ends;
the positioning cylinder (7) is arranged at the axial middle position of the two wedge-shaped circular plates (6), is arranged on the inner ring of the rolling bearing (8) in an interference fit manner in accordance with the wedge-shaped circular plates (6), and the width of the positioning cylinder (7) is slightly larger than that of the annular connecting piece (2);
the taper of the tapered roller (5) is the same as that of the end part of the rotor (1), but the tapered roller is arranged in the direction opposite to the inclined plane direction of the rotor (1), and a gap L1 with uniform size exists between the tapered roller (5) and the end part surface of the rotor (1) along the axial direction; in addition, the tapered roller (5) comprises more than 2 tapered roller split bodies (51), and each tapered roller split body (51) is distributed in a guide groove (4) arranged in the annular connecting piece (2) through roller shafts (52) arranged at two ends; meanwhile, the outer circle surface of the roller shaft (52) is contacted with the inner surface of the wedge-shaped circular plate (6).
2. A tapered roller type protective bearing device for simultaneously eliminating radial and axial clearances of a rotor according to claim 1, wherein: the number of the conical roller split bodies (51) is 2-200.
3. A tapered roller type protective bearing device for simultaneously eliminating radial and axial clearances of a rotor according to claim 1, wherein: the rolling bearing (8) is a deep groove ball bearing or a pair of angular contact bearings.
4. A tapered roller type protective bearing device for simultaneously eliminating radial and axial clearances of a rotor according to claim 1, wherein: the elastic supporting piece (3) is an independent spring element or a structure which is integrated with the annular connecting piece (2) and is processed by the processes of wire cutting and the like.
5. A tapered roller type protective bearing device for simultaneously eliminating radial and axial clearances of a rotor according to claim 1, wherein: bearing gland (9) are discoid, and the disc is equipped with the round screw hole along the circumference, and bearing gland (9) are pressed in the seam crossing of bearing frame (11) and antifriction bearing (9).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610142213.7A CN106168255B (en) | 2016-03-14 | 2016-03-14 | Taper roller formula eliminates the protection bearing arrangement of rotor footpath axial gap simultaneously |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610142213.7A CN106168255B (en) | 2016-03-14 | 2016-03-14 | Taper roller formula eliminates the protection bearing arrangement of rotor footpath axial gap simultaneously |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106168255A true CN106168255A (en) | 2016-11-30 |
| CN106168255B CN106168255B (en) | 2018-04-03 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610142213.7A Expired - Fee Related CN106168255B (en) | 2016-03-14 | 2016-03-14 | Taper roller formula eliminates the protection bearing arrangement of rotor footpath axial gap simultaneously |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106168255B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108443335A (en) * | 2018-05-30 | 2018-08-24 | 江苏理工学院 | Crank block type radial protection bearing |
| CN109654122A (en) * | 2019-01-02 | 2019-04-19 | 江苏理工学院 | A kind of protection bearing arrangement of the outer ring gap of adjustable bearings |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| IT1116082B (en) * | 1978-05-23 | 1986-02-10 | Nadella | RADIAL BEARING TO RESUME THE GAME |
| EP0412870A1 (en) * | 1989-08-10 | 1991-02-13 | Nadella | Prestressed radial rollbearing, especially for an automotive vehicle suspension |
| CN2823655Y (en) * | 2005-06-25 | 2006-10-04 | 攀枝花新钢钒股份有限公司 | Integral bearing seat capable of regulating bearing fastening force |
| JP2008138779A (en) * | 2006-12-01 | 2008-06-19 | Ntn Corp | Shaft supporting device and preload method for cylindrical roller bearing |
| CN102112760A (en) * | 2008-09-24 | 2011-06-29 | 三菱重工业株式会社 | Speed-up device for wind-driven generator and support mechanism for rotating shaft |
| CN103912589A (en) * | 2014-03-25 | 2014-07-09 | 南京航空航天大学 | Centripetal thrust protection bearing device for automatically eliminating clearance |
-
2016
- 2016-03-14 CN CN201610142213.7A patent/CN106168255B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| IT1116082B (en) * | 1978-05-23 | 1986-02-10 | Nadella | RADIAL BEARING TO RESUME THE GAME |
| EP0412870A1 (en) * | 1989-08-10 | 1991-02-13 | Nadella | Prestressed radial rollbearing, especially for an automotive vehicle suspension |
| CN2823655Y (en) * | 2005-06-25 | 2006-10-04 | 攀枝花新钢钒股份有限公司 | Integral bearing seat capable of regulating bearing fastening force |
| JP2008138779A (en) * | 2006-12-01 | 2008-06-19 | Ntn Corp | Shaft supporting device and preload method for cylindrical roller bearing |
| CN102112760A (en) * | 2008-09-24 | 2011-06-29 | 三菱重工业株式会社 | Speed-up device for wind-driven generator and support mechanism for rotating shaft |
| CN103912589A (en) * | 2014-03-25 | 2014-07-09 | 南京航空航天大学 | Centripetal thrust protection bearing device for automatically eliminating clearance |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108443335A (en) * | 2018-05-30 | 2018-08-24 | 江苏理工学院 | Crank block type radial protection bearing |
| CN108443335B (en) * | 2018-05-30 | 2024-04-05 | 江苏理工学院 | Crank sliding block type radial protection bearing |
| CN109654122A (en) * | 2019-01-02 | 2019-04-19 | 江苏理工学院 | A kind of protection bearing arrangement of the outer ring gap of adjustable bearings |
| CN109654122B (en) * | 2019-01-02 | 2020-05-05 | 江苏理工学院 | Protection bearing device in adjustable bearing inner race clearance |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106168255B (en) | 2018-04-03 |
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