CN114483785B - Large magnetic suspension sliding bearing capable of realizing vibration autonomous control - Google Patents
Large magnetic suspension sliding bearing capable of realizing vibration autonomous control Download PDFInfo
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- CN114483785B CN114483785B CN202210137062.1A CN202210137062A CN114483785B CN 114483785 B CN114483785 B CN 114483785B CN 202210137062 A CN202210137062 A CN 202210137062A CN 114483785 B CN114483785 B CN 114483785B
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- permanent magnet
- metal shaft
- bearing
- annular
- annular permanent
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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
- F16C32/00—Bearings not otherwise provided for
- F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
- F16C32/0406—Magnetic bearings
- F16C32/0408—Passive magnetic bearings
- F16C32/0423—Passive magnetic bearings with permanent magnets on both parts repelling each other
- F16C32/0425—Passive magnetic bearings with permanent magnets on both parts repelling each other for radial load mainly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
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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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/03—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using magnetic or electromagnetic means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Abstract
A large magnetic suspension sliding bearing for realizing vibration autonomous control belongs to the field of large industrial equipment and the technical field of mechanical design and manufacture. And the neck parts of the two ends of the metal shaft of the large magnetic suspension sliding bearing are sleeved with annular permanent magnets A and B. Permanent magnets A, B, C and D are uniformly distributed on the upper side, the lower side, the left side and the right side of the annular permanent magnet A, and the magnetic poles of the annular permanent magnet A and the four permanent magnets are opposite. Permanent magnets F, G, H and I are uniformly distributed on the upper, lower, left and right sides of the annular permanent magnet B, and the magnetic poles of the annular permanent magnet B are opposite to those of the four permanent magnets. The non-metal shaft sleeve is sleeved on the metal shaft, and a lubricant is filled between the metal shaft and the non-metal shaft sleeve. And a permanent magnet E is arranged above the non-metal shaft sleeve and used for attracting the metal shaft to enable the metal shaft to suspend. The invention adopts the radial repulsion action to restrain the radial low-frequency vibration of the bearing, improves the dynamic rigidity of the bearing support, reduces the integral friction and noise of the bearing and greatly improves the stable operation reliability of the bearing.
Description
Technical Field
The invention belongs to the field of large-scale industrial equipment and the technical field of mechanical design and manufacture, and relates to a large-scale magnetic suspension sliding bearing for realizing vibration autonomous control.
Background
The problem of vibration of a common sliding bearing always belongs to the problem of the world, particularly, when the bearing is started, a shaft neck is in direct contact with a shaft sleeve, the problems of friction and noise are serious, abrasion is easy to cause, and the service life of the bearing is seriously influenced. When the pure magnetic suspension bearing is adopted, the pure magnetic suspension bearing is difficult to apply in the field of large bearings due to huge power consumption and poor reliability. When the permanent magnetic adsorption technology is adopted to suspend the shaft neck, the running stability and the low-frequency vibration resistance of the bearing are poor.
In contrast, the invention adopts the combined action of permanent magnet adsorption and repulsion to balance the gravity and the load of the shaft neck, thereby greatly improving the reliability. The main purpose of adopting the radial repulsive force is to control the vibration of the bearing, improve the dynamic rigidity of the bearing support, further inhibit the vibration of the journal in the radial low frequency and reduce the integral friction and noise of the bearing.
Disclosure of Invention
The invention aims to establish an optimized design for realizing vibration autonomous control of a large-scale magnetic suspension sliding bearing based on the synergistic action of permanent magnet adsorption and repulsion, and the problem of poor low-frequency vibration resistance of the bearing is solved. The bearing has the outstanding characteristics that the gravity and the load of the shaft neck are balanced by adopting the combined action of the adsorption and the repulsion of the permanent magnet, the low-frequency vibration of the bearing is inhibited, and the running stability of the bearing is further improved.
In order to achieve the purpose, the technical scheme of the invention is as follows:
the large magnetic suspension sliding bearing comprises a permanent magnet A1, a permanent magnet B2, a permanent magnet C3, a permanent magnet D4, an annular permanent magnet A5, a metal shaft 6, a permanent magnet E7, a non-metal shaft sleeve 8, a lubricant 9, a permanent magnet F10, a permanent magnet G11, a permanent magnet H12, a permanent magnet I13 and an annular permanent magnet B14.
And the shaft necks at the two ends of the metal shaft 6 are sleeved with an annular permanent magnet A5 and an annular permanent magnet B14, wherein the magnetic poles of the annular permanent magnet A5 and the annular permanent magnet B14 are the same. The upper part, the lower part, the left part and the right part of the annular permanent magnet A5 are uniformly distributed with a permanent magnet A1, a permanent magnet B2, a permanent magnet C3 and a permanent magnet D4, and the annular permanent magnet A5 has opposite magnetic poles with the permanent magnet A1, the permanent magnet B2, the permanent magnet C3 and the permanent magnet D4 and is repulsive force. Similarly, the permanent magnet F10, the permanent magnet G11, the permanent magnet H12 and the permanent magnet I13 are uniformly distributed on the upper, lower, left and right sides of the annular permanent magnet B14, and the annular permanent magnet B14 is opposite to the permanent magnet F10, the permanent magnet G11, the permanent magnet H12 and the permanent magnet I13 in magnetic poles and is repulsive force. The non-metal shaft sleeve 8 is sleeved on the metal shaft 6, and a lubricant 9 is filled between the metal shaft 6 and the non-metal shaft sleeve 8. And a permanent magnet E7 is arranged above the non-metal shaft sleeve 8, and the permanent magnet E7 is used for attracting the metal shaft 6 to enable the metal shaft 6 to suspend.
The radial rigidity of the shaft neck position repulsive forces at the two ends of the metal shaft 6 is greater than the dynamic rigidity of the bearing lubricant 9 and the radial rigidity of the permanent magnet E7 to the attraction force of the metal shaft 6 at the bearing working position, and the larger the radial rigidity of the shaft neck position repulsive forces at the two ends of the metal shaft 6 is, the better the vibration resistance effect is.
When in use, the metal shaft 6 is attracted by the permanent magnet E7 and suspended in the lubricant 9 filled in the non-metal shaft sleeve 8. When the sliding bearing runs, the shaft neck parts at the two ends of the metal shaft 6 are in a balanced state due to the repulsive force between the permanent magnets, and the stable running of the bearing is ensured. When the bearing bears radial low-frequency vibration, the shaft necks at the two ends of the metal shaft 6 deviate from the balance position, however, the shaft necks at the two ends of the metal shaft 6 push the two ends of the metal shaft 6 back to the balance position again due to the mutual repulsion action between the permanent magnets, so that the vibration of the bearing is inhibited, and the bearing operates stably again.
Further, the permanent magnets mutually repelling the annular permanent magnet A5 and the annular permanent magnet B14 may be 4 symmetrical structures along the circumferential direction, or may be more symmetrical structures or annular structures.
Compared with the prior art, the invention has the beneficial effects that:
the invention adopts the radial repulsion action to inhibit the radial low-frequency vibration of the bearing, improves the dynamic rigidity of the bearing support, reduces the integral friction and noise of the bearing and greatly improves the stable operation reliability of the bearing.
Drawings
FIG. 1 is a schematic sectional front view of a large magnetic suspension sliding bearing with vibration self-control;
FIG. 2 is a schematic side sectional view of a bearing journal A;
FIG. 3 is a schematic side cross-sectional view of a bearing journal C;
fig. 4 is a schematic side sectional view of the bearing B.
In the figure: the permanent magnet comprises a permanent magnet A1, a permanent magnet B2, a permanent magnet C3, a permanent magnet D4, an annular permanent magnet A5, a metal shaft 6, a permanent magnet E7, a non-metal shaft sleeve 8, a lubricant 9, a permanent magnet F10, a permanent magnet G11, a permanent magnet H12, a permanent magnet I13 and an annular permanent magnet B14.
Detailed Description
The present invention is further illustrated by the following specific examples.
The large magnetic suspension sliding bearing comprises a permanent magnet A1, a permanent magnet B2, a permanent magnet C3, a permanent magnet D4, an annular permanent magnet A5, a metal shaft 6, a permanent magnet E7, a non-metal shaft sleeve 8, a lubricant 9, a permanent magnet F10, a permanent magnet G11, a permanent magnet H12, a permanent magnet I13 and an annular permanent magnet B14.
And the neck parts of the two ends of the metal shaft 6 are sleeved with an annular permanent magnet A5 and an annular permanent magnet B14. The upper part, the lower part, the left part and the right part of the annular permanent magnet A5 are uniformly distributed with a permanent magnet A1, a permanent magnet B2, a permanent magnet C3 and a permanent magnet D4, and the annular permanent magnet A5 has opposite magnetic poles with the permanent magnet A1, the permanent magnet B2, the permanent magnet C3 and the permanent magnet D4 and is repulsive force. Similarly, the permanent magnet F10, the permanent magnet G11, the permanent magnet H12 and the permanent magnet I13 are uniformly distributed on the upper, lower, left and right sides of the annular permanent magnet B14, and the annular permanent magnet B14 is opposite to the permanent magnet F10, the permanent magnet G11, the permanent magnet H12 and the permanent magnet I13 in magnetic poles and is repulsive force. The non-metal shaft sleeve 8 is sleeved on the metal shaft 6, and a lubricant 9 is filled between the metal shaft 6 and the non-metal shaft sleeve 8. A permanent magnet E7 is arranged above the non-metal shaft sleeve 8, and the permanent magnet E7 is used for attracting the metal shaft 6 to enable the metal shaft 6 to suspend. The permanent magnets which are mutually repelled with the annular permanent magnet A5 and the annular permanent magnet B14 are in 4 symmetrical structures along the circumferential direction.
When in use, the metal shaft 6 is attracted by the permanent magnet E7 and suspended in the lubricant 9 filled in the non-metal shaft sleeve 8. When the sliding bearing runs, the shaft neck parts at the two ends of the metal shaft 6 are in a balanced state due to the repulsive force between the permanent magnets, and the stable running of the bearing is ensured. When the bearing bears radial low-frequency vibration, the shaft necks at the two ends of the metal shaft 6 deviate from the balance position, however, the shaft necks at the two ends of the metal shaft 6 push the two ends of the metal shaft 6 back to the balance position again due to mutual repulsion between the permanent magnets, so that the vibration of the bearing is inhibited, and the bearing operates stably again.
The above-mentioned embodiments only represent the embodiments of the present invention, but they should not be understood as the limitation of the scope of the present invention, and it should be noted that those skilled in the art can make several variations and modifications without departing from the spirit of the present invention, and these all fall into the protection scope of the present invention.
Claims (2)
1. A large magnetic suspension sliding bearing for realizing vibration autonomous control is characterized by comprising a permanent magnet A (1), a permanent magnet B (2), a permanent magnet C (3), a permanent magnet D (4), an annular permanent magnet A (5), a metal shaft (6), a permanent magnet E (7), a non-metal shaft sleeve (8), a permanent magnet F (10), a permanent magnet G (11), a permanent magnet H (12), a permanent magnet I (13) and an annular permanent magnet B (14);
the shaft necks at the two ends of the metal shaft (6) are sleeved with an annular permanent magnet A (5) and an annular permanent magnet B (14), wherein the annular permanent magnet A (5) and the annular permanent magnet B (14) are completely the same; permanent magnets A (1), B (2), C (3) and D (4) are uniformly distributed on the upper, lower, left and right sides of the annular permanent magnet A (5), and the annular permanent magnet A (5) is opposite to the magnetic poles of the permanent magnets A (1), B (2), C (3) and D (4) and is repulsive; the permanent magnet F (10), the permanent magnet G (11), the permanent magnet H (12) and the permanent magnet I (13) are uniformly distributed on the upper side, the lower side, the left side and the right side of the annular permanent magnet B (14), and the annular permanent magnet B (14) is opposite to the magnetic poles of the permanent magnet F (10), the permanent magnet G (11), the permanent magnet H (12) and the permanent magnet I (13) and is repulsive; the non-metal shaft sleeve (8) is sleeved on the metal shaft (6), and a lubricant (9) is filled between the metal shaft (6) and the non-metal shaft sleeve (8); a permanent magnet E (7) used for suspending the metal shaft (6) is arranged above the non-metal shaft sleeve (8).
2. A large-sized magnetic suspension sliding bearing for realizing vibration autonomous control according to claim 1, characterized in that the radial rigidity of the shaft neck position repulsive force at the two ends of the metal shaft (6) is larger than the dynamic rigidity of the bearing lubricant (9) and the radial rigidity of the permanent magnet E (7) to the attraction force of the metal shaft (6) at the bearing working position, and the larger the radial rigidity of the shaft neck position repulsive force at the two ends of the metal shaft (6), the better the vibration resistance effect.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210137062.1A CN114483785B (en) | 2022-02-15 | 2022-02-15 | Large magnetic suspension sliding bearing capable of realizing vibration autonomous control |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210137062.1A CN114483785B (en) | 2022-02-15 | 2022-02-15 | Large magnetic suspension sliding bearing capable of realizing vibration autonomous control |
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| Publication Number | Publication Date |
|---|---|
| CN114483785A CN114483785A (en) | 2022-05-13 |
| CN114483785B true CN114483785B (en) | 2022-10-04 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210137062.1A Active CN114483785B (en) | 2022-02-15 | 2022-02-15 | Large magnetic suspension sliding bearing capable of realizing vibration autonomous control |
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03134311A (en) * | 1989-10-20 | 1991-06-07 | Ntn Corp | Magnetic bearing device |
| CN106640966A (en) * | 2017-02-17 | 2017-05-10 | 燕山大学 | Magnetic fluid double suspension driving and driven radial bearing |
| CN107191488A (en) * | 2017-07-03 | 2017-09-22 | 燕山大学 | A kind of magnetic liquid dual suspension passive bearing journal bearing |
| CN110332235A (en) * | 2019-06-21 | 2019-10-15 | 山东科技大学 | A kind of passive type permanent magnet expulsive force type magnetic axis bearing structure |
| CN113048150A (en) * | 2021-02-18 | 2021-06-29 | 武汉理工大学 | Large-bearing magnetic-liquid double-floating radial bearing with magnetic gradient and array arrangement |
-
2022
- 2022-02-15 CN CN202210137062.1A patent/CN114483785B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03134311A (en) * | 1989-10-20 | 1991-06-07 | Ntn Corp | Magnetic bearing device |
| CN106640966A (en) * | 2017-02-17 | 2017-05-10 | 燕山大学 | Magnetic fluid double suspension driving and driven radial bearing |
| CN107191488A (en) * | 2017-07-03 | 2017-09-22 | 燕山大学 | A kind of magnetic liquid dual suspension passive bearing journal bearing |
| CN110332235A (en) * | 2019-06-21 | 2019-10-15 | 山东科技大学 | A kind of passive type permanent magnet expulsive force type magnetic axis bearing structure |
| CN113048150A (en) * | 2021-02-18 | 2021-06-29 | 武汉理工大学 | Large-bearing magnetic-liquid double-floating radial bearing with magnetic gradient and array arrangement |
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| Publication number | Publication date |
|---|---|
| CN114483785A (en) | 2022-05-13 |
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