CN109681523B - Combined sliding surface spiral groove bearing - Google Patents
Combined sliding surface spiral groove bearing Download PDFInfo
- Publication number
- CN109681523B CN109681523B CN201910084185.1A CN201910084185A CN109681523B CN 109681523 B CN109681523 B CN 109681523B CN 201910084185 A CN201910084185 A CN 201910084185A CN 109681523 B CN109681523 B CN 109681523B
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- Prior art keywords
- oil
- bearing
- rotating shaft
- bearing bush
- sliding
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Classifications
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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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
- F16C17/24—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with devices affected by abnormal or undesired positions, e.g. for preventing overheating, for safety
- F16C17/243—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with devices affected by abnormal or undesired positions, e.g. for preventing overheating, for safety related to temperature and heat, e.g. for preventing overheating
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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
- F16C33/16—Sliding surface consisting mainly of graphite
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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
- F16C37/00—Cooling of bearings
-
- 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
- F16C2202/00—Solid materials defined by their properties
- F16C2202/50—Lubricating properties
-
- 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
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/20—Application independent of particular apparatuses related to type of movement
- F16C2300/22—High-speed rotation
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
The invention discloses a combined sliding surface spiral groove bearing, which comprises a bearing bush and a rotating shaft, wherein the rotating shaft is arranged in the bearing bush, and the rotating shaft is in clearance fit with the bearing bush. In the use state, the axle center of the rotating shaft is positioned below one side of the axle center of the bearing bush, and the gap between the bearing bush and the rotating shaft forms a converging area and a diverging area of oil along the rotating direction of the rotating shaft. The inner wall of the bearing bush is sequentially provided with a plurality of oil cavities at intervals along the circumferential direction, and an oil inlet and an oil outlet are arranged in each oil cavity. The sliding coating areas are arranged in all the oil cavities, the sliding coating areas in the oil cavities in the convergence area extend along the rotation direction of the rotating shaft, and sliding coating extension areas are formed on the inner wall of the bearing bush. The coating of the sliding coating area and the sliding coating extension area is fluorocarbon coating. According to the invention, by utilizing the sliding characteristic of the fluorocarbon coating, the friction resistance is reduced, the friction power consumption in an oil film is reduced, the oil film pressure and the end leakage are improved, the heat is taken away rapidly, the temperature rise in the high-speed rotation process of the bearing is inhibited, and the bearing capacity for the high-speed rotation of the bearing is improved.
Description
Technical Field
The invention relates to the technical field of bearings, in particular to a combined sliding surface spiral groove bearing.
Background
High-speed and ultra-high-speed cutting is becoming the main stream of development of cutting technology and machine tools, and bearings as important supporting modes become important factors affecting the speed and stability of the machine tools. The liquid dynamic and static pressure bearing has high bearing capacity, high rigidity and high rotation precision, and has great application potential in high-speed rotating machinery. The heating is the root cause for restricting the increase of the rotation speed of the dynamic and static pressure bearing, when the rotation speed is increased, the friction power consumption in the oil film is obviously increased, so that the temperature rise of the oil film is increased, and even the 'shaft locking' accident is caused when the temperature rise is serious. The problem of temperature rise is one of the main difficulties in the field of fluid lubrication.
The existing method for reducing the temperature rise often adopts the traditional dynamic and static pressure sliding bearing design technology lubricated by low-viscosity lubricating medium, and the bearings designed by the traditional method often need to be researched and tested for finding out the performance advantages and defects of the bearings through a long period. In order to maximally utilize the advantages of the existing bearing and make the bearing better applied to high-speed and ultra-high-speed rotating machinery, the temperature rise of the bearing is required to be controlled. The working performance of the bearing bush contact surface is enhanced through a surface spraying technology, so that the method has become an effective means for improving the bearing working performance, and has important significance for optimizing the sliding bearing performance, improving the working efficiency and stability of a mechanical system, promoting the innovation development of the machinery and the like.
Disclosure of Invention
Aiming at the defects of the prior art, the invention aims to provide a combined sliding surface spiral groove bearing, which solves the problems that the bearing capacity of the bearing is poor and the temperature rise of the bearing is difficult to control in the high-speed running process of the bearing due to the remarkable increase of friction power consumption in an oil film caused by overlarge resistance of lubricating oil between a bearing bush and a rotating shaft.
In order to solve the technical problems, the invention adopts the following technical scheme:
the utility model provides a combination sliding surface helical groove bearing, includes axle bush and pivot, the pivot sets up in the axle bush, pivot and axle bush clearance fit. In the use state, the axle center of the rotating shaft is positioned below one side of the axle center of the bearing bush, and the gap between the bearing bush and the rotating shaft forms a converging area and a diverging area of oil along the rotating direction of the rotating shaft. The inner wall of the bearing bush is sequentially provided with a plurality of oil cavities at intervals along the circumferential direction, and an oil inlet and an oil outlet are arranged in each oil cavity. The inner walls of all the oil cavities are provided with sliding coating areas, the sliding coating areas in all the oil cavities are positioned in the convergence area, the inner walls of the oil cavities extend out along the rotation direction of the rotating shaft, and sliding coating extension areas are formed on the inner walls of the bearing bushes.
Preferably, the opening of the oil cavity on the inner wall of the bearing bush is parallelogram, and the bottom of the oil cavity is in an arc structure with high ends and low middle along the circumferential direction. The oil inlet and the oil outlet are arranged at the lowest part of the bottom of the oil cavity and distributed at two ends of the oil cavity along the axial direction of the bearing bush.
Preferably, a side of the opening of the oil chamber near the oil outlet is inclined toward the rotation direction of the rotating shaft with respect to a side of the oil inlet thereof.
Preferably, the sliding coating area covers the bottom of the oil cavity, is deviated to one side of the rotating direction of the rotating shaft from the connecting line position of the oil inlet and the oil outlet, and extends to the edge of the opening of the oil cavity.
Preferably, the sliding coating extending area covers the inner surface of the bearing bush, the outer contour of the sliding coating extending area is in a right trapezoid shape, and an included angle between the inclined side of the sliding coating extending area and the rotating direction of the rotating shaft is 5-8 degrees.
Preferably, there are at least two slip coating extensions located in the convergence region, and the circumferential length of each slip coating extension decreases in sequence in the rotation direction of the rotating shaft from the maximum gap between the bearing bush and the rotating shaft to the minimum gap. The first sliding coating extending area is positioned in the convergence area and extends to the opening of the adjacent oil cavity along the rotating direction of the rotating shaft.
Preferably, the coating of the slip coating zone and the slip coating extension zone is a fluorocarbon coating.
Preferably, the oil inlet and the oil outlet are respectively close to two ends of the oil cavity along the axial direction of the bearing bush.
By adopting the technical scheme, the invention has the beneficial technical effects that: the invention utilizes the sliding characteristic of the fluorocarbon coating to reduce the friction resistance of lubricating oil flow, reduce the friction power consumption in an oil film, improve the pressure and the end leakage of the oil film, quickly take away heat, inhibit the temperature rise of the bearing in the high-speed running process and improve the bearing capacity for the bearing in the high-speed running process.
Drawings
FIG. 1 is a schematic diagram of the structural principle of a combined sliding surface helical groove bearing of the present invention.
Fig. 2 is a schematic view of the bearing shell of fig. 1 in a circumferentially expanded configuration.
Detailed Description
The invention is described in detail below with reference to the attached drawing figures:
referring to fig. 1 and 2, a combined sliding surface spiral groove bearing comprises a bearing bush 1 and a rotating shaft 2, wherein the rotating shaft 2 is arranged in the bearing bush 1, the bearing bush 1 is fixedly arranged on a bearing seat, the rotating shaft 2 is in clearance fit with the bearing bush 1, the bearing bush 1 can be a split bearing bush or an integral bearing bush, and the invention preferably adopts an integral bearing bush. In the use state, the rotating shaft 2 rotates at a high speed at the inner side of the bearing bush 1, and the gap between the rotating shaft 2 and the bearing bush 1 is filled with lubricating oil, so that an oil film in a motion state is formed by the lubricating oil. The axle center of the rotating shaft 2 running at high speed is positioned at one side of the axle center of the bearing bush 1, the gap between the bearing bush 1 and the rotating shaft 2 forms a convergence zone 3 and a divergence zone 4 of an oil film along the rotating direction of the rotating shaft 2, and the gap between the rotating shaft 2 and the bearing bush 1 is divided into two parts at the minimum gap 9 and the maximum gap between the rotating shaft 2 and the bearing bush 1, wherein one part is the convergence zone 3, and the other part is the divergence zone 4. Specifically, when the rotating shaft 2 rotates anticlockwise, the axis of the rotating shaft 2 is located below the right side of the axis of the bearing bush 1, and when the rotating shaft 2 rotates clockwise, the axis of the rotating shaft 2 is located below the left side of the axis of the bearing bush 1.
The inner wall of the bearing bush 1 is provided with three oil cavities, namely a first oil cavity 11, a second oil cavity 12 and a third oil cavity 13, which are sequentially distributed at intervals along the circumferential direction of the bearing bush 1, wherein the first oil cavity 11 is positioned in a divergent region 4 of an oil film, and the second oil cavity 12 and the third oil cavity 13 are both positioned in a convergent region 3 of the oil film. The openings of the oil chambers on the inner wall of the bearing bush 1 are parallelograms, and the bottoms of the first oil chamber 11, the second oil chamber 12 and the third oil chamber 13 are arc structures with high ends and low middle parts along the circumferential direction. The first oil cavity 11, the second oil cavity 12 and the third oil cavity 13 are respectively provided with an oil inlet 7 and an oil outlet 8, wherein the oil inlet 7 and the oil outlet 8 are arranged at the lowest part of the bottom of the oil cavity and are distributed at two ends of the oil cavity along the axial direction of the bearing bush 1. The side of the opening of the oil cavity, which is close to the oil outlet 8, is inclined towards the rotation direction of the rotating shaft 2 relative to the side of the oil inlet 7.
Taking one oil cavity as an example, the movement of an oil film in a working state is described: lubricating oil enters the oil cavity through the oil inlet 7, moves in the oil cavity along the rotation direction of the rotating shaft 2, diverges to one side close to the oil outlet 8, enters a gap between the rotating shaft 2 and the bearing bush 1, and moves along the rotation direction of the rotating shaft 2. When the oil film in the gap between the rotating shaft 2 and the bearing bush 1 moves to the oil cavity along the rotating direction of the rotating shaft 2, part of the oil film close to the surface layer of the bearing bush 1 enters the oil cavity, moves in the oil cavity along the rotating direction of the rotating shaft 2 and converges to one side close to the oil outlet 8, the bearing bush 1 is discharged from the oil outlet 8, and a large amount of heat is taken away by the lubricating oil discharged from the oil outlet 8, so that the purpose of cooling is achieved.
The bottoms of the three oil cavities are respectively provided with a sliding coating area 5, and the sliding coating areas 5 cover the connecting line positions of the oil cavities, which are positioned at the oil inlets 7 and the oil outlets 8, to deviate to one side of the rotating shaft 2 in the rotating direction and extend to the edge of the opening of the oil cavity. The sliding coating areas in the second oil cavity 12 and the third oil cavity 13 in the convergence area extend out of the corresponding oil cavities along the rotation direction of the rotating shaft 2, a sliding coating extending area 6 is formed on the inner wall of the bearing bush 1, and the coatings of the sliding coating area 5 and the sliding coating extending area 6 are fluorocarbon coatings. The sliding coating extending area 6 covers the inner surface of the bearing bush 1, the outer contour of the sliding coating extending area is a right trapezoid, and the included angle between the inclined edge of the sliding coating extending area 6 and the rotating direction of the rotating shaft 2 is 7 degrees. Under the operating condition, lubricating oil enters each oil cavity through the oil inlet 7, is close to the lubricating oil in the sliding coating area 5, quickly slides from the oil cavity into the gap between the rotating shaft 2 and the bearing bush 1 along the rotating direction of the rotating shaft 2, the sliding coating area 5 effectively reduces the resistance of the inner wall of the oil cavity to the movement of the lubricating oil, and improves the flow velocity of the lubricating oil in the oil cavity by utilizing the characteristic that the adhesive force of the lubricating oil on the fluorocarbon coating surface is poor.
The sliding coating extending areas 6 corresponding to the second oil cavity 12 and the third oil cavity 13 are respectively provided with one, the circumferential length of each sliding coating extending area 6 is sequentially reduced from the maximum clearance position to the minimum clearance position 9 of the bearing bush 1 and the rotating shaft 2 along the rotating direction of the rotating shaft 2, namely, the circumferential length of the sliding coating extending area 6 corresponding to the second oil cavity 12 is larger than that of the sliding coating extending area 6 corresponding to the third oil cavity 13, and the sliding coating extending area 6 (namely, the sliding coating extending area 6 corresponding to the second oil cavity 12) which is positioned in the convergence area and is positioned at the first time along the rotating direction of the rotating shaft 2 extends to the opening position of the third oil cavity 13. The lubricating oil moves along with the rotating shaft after entering the gap between the rotating shaft 2 and the bearing bush 1 from the oil cavity, the flow velocity of the lubricating oil in the convergence zone 3 is obviously lower than that of the lubricating oil in the divergence zone, and the sliding coating extension zone 6 in the convergence zone 3 can effectively reduce the resistance of the bearing bush surface to the lubricating oil and improve the flow velocity of the lubricating oil in the convergence zone 3 and the flow velocity of the lubricating oil in the gap between the whole rotating shaft 2 and the bearing bush 1.
Under the condition of ensuring that the viscosity of the lubricating oil is unchanged, the invention utilizes the sliding characteristics of the fluorocarbon coating and the lubricating oil to improve the flow velocity of the lubricating oil in the rotating shaft 2 and the bearing bush 1, particularly the flow velocity in the convergence zone 3, obviously improve the oil film pressure, the bearing capacity and the end leakage, reduce the friction resistance of the flowing lubricating oil, obviously increase the friction power consumption in the oil film, quickly take away the heat, inhibit the temperature rise in the high-speed running process of the bearing and improve the bearing capacity of the bearing for high-speed rotation of the bearing, thus combining the proposal of the sliding surface spiral groove bearing, not only improving the bearing capacity of the bearing, but also solving the problem of controlling the temperature rise of the lubricating oil in the high-speed processing process.
It should be understood that the above description is not intended to limit the invention to the particular embodiments disclosed, but to limit the invention to the particular embodiments disclosed, and that the invention is not limited to the particular embodiments disclosed, but is intended to cover modifications, adaptations, additions and alternatives falling within the spirit and scope of the invention.
Claims (8)
1. The combined sliding surface spiral groove bearing comprises a bearing bush and a rotating shaft, and is characterized in that the rotating shaft is arranged in the bearing bush and is in clearance fit with the bearing bush;
in the use state, the axle center of the rotating shaft is positioned below one side of the axle center of the bearing bush, and the gap between the bearing bush and the rotating shaft forms a converging area and a diverging area of oil along the rotating direction of the rotating shaft;
the inner wall of the bearing bush is sequentially provided with a plurality of oil cavities at intervals along the circumferential direction, and an oil inlet and an oil outlet are arranged in each oil cavity;
the inner walls of all the oil cavities are provided with sliding coating areas, the sliding coating areas in all the oil cavities are positioned in the convergence area, the inner walls of the oil cavities extend out along the rotation direction of the rotating shaft, and sliding coating extension areas are formed on the inner walls of the bearing bushes.
2. The combined sliding surface spiral groove bearing of claim 1, wherein the opening of the oil cavity on the inner wall of the bearing bush is parallelogram, and the bottom of the oil cavity is in an arc structure with high ends and low middle along the circumferential direction;
the oil inlet and the oil outlet are arranged at the lowest part of the bottom of the oil cavity and distributed at two ends of the oil cavity along the axial direction of the bearing bush.
3. A combined sliding surface helical groove bearing according to claim 2, wherein the side of the opening of the oil chamber near the oil outlet is inclined in the rotation direction of the rotary shaft with respect to the side of the oil inlet thereof.
4. The combination sliding surface helical groove bearing of claim 1, wherein the sliding coating area covers the bottom of the oil chamber, is biased to one side of the rotation direction of the rotation shaft from the connection position of the oil inlet and the oil outlet, and extends to the opening edge of the oil chamber.
5. A combined sliding surface helical groove bearing according to claim 1, wherein the sliding coating extension covers the inner surface of the bearing bush, the outer profile of which is right trapezoid, and the angle between the oblique side of the sliding coating extension and the rotation direction of the rotating shaft is 5 ° to 8 °.
6. The combination sliding surface helical groove bearing of claim 1, wherein there are at least two sliding coating extending areas in the converging area, the circumferential length of each sliding coating extending area decreasing in turn in the direction of rotation of the shaft from the maximum clearance between the bearing shell and the shaft to the minimum clearance;
the first sliding coating extending area is positioned in the convergence area and extends to the opening of the adjacent oil cavity along the rotating direction of the rotating shaft.
7. A combined sliding surface helical groove bearing according to claim 1 wherein the coating of the sliding coating region and the sliding coating extension region is a fluorocarbon coating.
8. The combination sliding surface helical groove bearing of claim 1, wherein said oil inlet and oil outlet are located near the ends of the oil chamber along the axial direction of the bearing shell, respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910084185.1A CN109681523B (en) | 2019-01-29 | 2019-01-29 | Combined sliding surface spiral groove bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910084185.1A CN109681523B (en) | 2019-01-29 | 2019-01-29 | Combined sliding surface spiral groove bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109681523A CN109681523A (en) | 2019-04-26 |
| CN109681523B true CN109681523B (en) | 2023-09-15 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910084185.1A Active CN109681523B (en) | 2019-01-29 | 2019-01-29 | Combined sliding surface spiral groove bearing |
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| Country | Link |
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| CN (1) | CN109681523B (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101696714A (en) * | 2009-10-23 | 2010-04-21 | 西安交通大学 | Water lubrication dynamic and static pressure ladder groove step bearing |
| CN104613094A (en) * | 2015-01-30 | 2015-05-13 | 江苏科技大学 | Multi-layer composite bearing bush sliding bearing with oil filling chamber |
| CN107387548A (en) * | 2017-08-29 | 2017-11-24 | 山东大学 | Archimedes' helicoid hydrodynamic sliding bearing and application |
| CN107795577A (en) * | 2017-11-22 | 2018-03-13 | 中车集团台州第七八六工厂 | A kind of bush(ing) bearing |
| CN208203802U (en) * | 2018-05-22 | 2018-12-07 | 新乡市海山机械有限公司 | A kind of anticorrosion bearing shell |
| CN210153086U (en) * | 2019-01-29 | 2020-03-17 | 山东科技大学 | Combined sliding surface spiral groove bearing |
-
2019
- 2019-01-29 CN CN201910084185.1A patent/CN109681523B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101696714A (en) * | 2009-10-23 | 2010-04-21 | 西安交通大学 | Water lubrication dynamic and static pressure ladder groove step bearing |
| CN104613094A (en) * | 2015-01-30 | 2015-05-13 | 江苏科技大学 | Multi-layer composite bearing bush sliding bearing with oil filling chamber |
| CN107387548A (en) * | 2017-08-29 | 2017-11-24 | 山东大学 | Archimedes' helicoid hydrodynamic sliding bearing and application |
| CN107795577A (en) * | 2017-11-22 | 2018-03-13 | 中车集团台州第七八六工厂 | A kind of bush(ing) bearing |
| CN208203802U (en) * | 2018-05-22 | 2018-12-07 | 新乡市海山机械有限公司 | A kind of anticorrosion bearing shell |
| CN210153086U (en) * | 2019-01-29 | 2020-03-17 | 山东科技大学 | Combined sliding surface spiral groove bearing |
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| Publication number | Publication date |
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| CN109681523A (en) | 2019-04-26 |
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