CN111637161B - Forced lubrication bearing with distributed pores - Google Patents
Forced lubrication bearing with distributed pores Download PDFInfo
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- CN111637161B CN111637161B CN202010420796.1A CN202010420796A CN111637161B CN 111637161 B CN111637161 B CN 111637161B CN 202010420796 A CN202010420796 A CN 202010420796A CN 111637161 B CN111637161 B CN 111637161B
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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
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/02—Sliding-contact bearings
- F16C25/04—Sliding-contact bearings self-adjusting
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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
- F16N—LUBRICATING
- F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
- F16N7/38—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with a separate pump; Central lubrication systems
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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
- F16N—LUBRICATING
- F16N2210/00—Applications
- F16N2210/14—Bearings
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
The invention provides a forced lubrication bearing with distributed pores. The bearing body is internally provided with a header pipe, the bearing body is provided with pressurizing holes leading to the inner surface of the bearing body along the axial direction and the circumferential direction, all the pressurizing holes are converged in the header pipe inside the bearing body, the header pipe is connected with a pressure servo mechanism through a pipeline, the bearing body is expanded along the circumferential direction, then the pressurizing holes are in an MXN grid, the distances between the pressurizing holes along the axial direction and the circumferential direction are unevenly distributed, and the distance between the pressurizing holes close to the maximum pressure point is gradually reduced. The pressure servo mechanism is started when detecting that the shafting is in a low-speed running condition, and the pressurizing medium is forcibly injected below the running shafting through the pressurizing hole, so that the pressurizing medium sprayed out of the pressurizing hole lifts the position with larger shafting load, and a liquid film is always formed between the shafting and the bearing under the condition of rotation, thereby improving the poor lubrication state of the bearing and relieving the friction and wear of the bearing.
Description
Technical Field
The invention relates to a radial sliding bearing, in particular to a radial sliding bearing with forced lubrication.
Background
The radial sliding bearing has the advantages of large bearing capacity, good adaptability and the like, is widely applied to rotary components of ships and machinery, and for the application fields, the control of the operation cost and the increase of the service life of the bearing are the primary conditions for selecting the bearing, so that the reduction of the frictional wear of a bearing system is an important index which is preferably considered in the bearing design. Under the rated operation condition of a shaft system, the shaft and the bearing are separated by a layer of liquid film, the friction coefficient is not large due to the shearing action of the liquid film, and the shaft and the bearing which operate in the hydrodynamic pressure lubrication stage have little abrasion and can be almost ignored. However, when the equipment is started and is in a working condition of higher load and lower rotating speed, such as a low-speed sailing stage of a ship, particularly a starting stage of a shafting of the ship, a shaft is in contact with a bearing part or even in direct contact, the bearing is in a mixed lubrication or boundary lubrication state, the friction coefficient of the bearing is very large at the moment, and if the load of the bearing is higher under the condition, the bearing is seriously abraded, which is a problem that a user of the equipment avoids as much as possible and is difficult to avoid. The invention mainly solves the problem of how to avoid the friction of the bearing under the condition of low speed and heavy load and ensure that the bearing runs in a better lubricating state as much as possible.
At present, domestic colleges and universities and research institutions pay more attention to analysis and control of bearing lubrication characteristics, and by means of simulation and test means, a plurality of methods are adopted to control the lubrication characteristics of the radial sliding bearing. The current general design concept focuses on two aspects: firstly, research is carried out from the material perspective to improve and enhance the material characteristics, and a wear-resistant and hard new material and the like are adopted; secondly, the structural optimization developed from the bearing structure angle adopts novel bearing structure, such as changing axle bush thickness, axle bush structure, pipe chute bearing, spiral slot type lubricating structure etc..
In the 'design of a water-lubricated rubber bearing structure' in the article '2011 vol.33 of ship science and technology', the optimization research on the water-lubricated rubber bearing structure mainly focuses on the research on the influence of the bearing structure on a hydrodynamic lubrication state, such as structural factors of the cross-sectional shape of a bearing bush, the thickness of a bearing bush rubber layer, the arrangement form of the bearing bush and the like, and results show that the friction coefficient of the normal operation of the bearing can be reduced by reducing the thickness of the bearing bush rubber layer and the arrangement form of the arrangement of the bottom of the bearing into a water flowing groove.
In the article of 'dynamic pressure lubrication characteristic and dynamic contact finite element simulation analysis of spiral groove water lubrication rubber alloy bearing' of university of Chongqing, the spiral groove water lubrication rubber bearing is taken as a research object, a dynamic pressure lubrication mechanism is combined, the dynamic pressure characteristic of the bearing is researched, the influence rule of parameters such as rotating speed, eccentricity, transition fillet, spiral angle, groove number and the like on parameters such as liquid film pressure is given, and the method has reference significance for further optimization of the spiral groove water lubrication rubber alloy bearing.
In the patent document entitled "water-lubricated hydrostatic stern bearing for ship", a pressure water outlet groove with gradually increasing length is formed on the inner surface of the lower part of a bearing lining, so that high-pressure water flows between the lining and a stern shaft to form a water film and reduce the direct contact area, thereby achieving the purpose of reducing frictional vibration and providing reference for the optimized design of the stern bearing for the ship.
In the published publications, new concepts have been proposed for bearing structures. However, in practical situations, the contact force distribution of the radial sliding bearing and the shafting should satisfy the reynolds equation, rather than simply increasing or decreasing from head to tail, and the pressure distribution is about distributed in the form of a high-order polynomial of the bearing length L from the maximum bearing position of the bearing to both sides.
Disclosure of Invention
The invention aims to provide a forced lubrication bearing with distributed pores, which can improve the lubrication state of a radial sliding bearing and can forcibly generate a targeted lubricating liquid film under the low-speed running working condition of a shafting.
The purpose of the invention is realized as follows:
the bearing body is internally provided with a header pipe, the bearing body is provided with pressurizing holes leading to the inner surface of the bearing body along the axial direction and the circumferential direction, all the pressurizing holes are converged in the header pipe inside the bearing body, the header pipe is connected with a pressure servo mechanism through a pipeline, the bearing body is expanded along the circumferential direction, then the pressurizing holes are in an MXN grid, the distances between the pressurizing holes along the axial direction and the circumferential direction are unevenly distributed, and the distance between the pressurizing holes close to the maximum pressure point is gradually reduced.
The present invention may further comprise:
1. the pressure servo mechanism is formed by connecting a pipeline, a pump, a control valve and a control system, the control system is triggered, the control valve is opened and the pump is instructed to work under the condition that the shaft system runs at a low speed, a pressurized medium is injected into the bearing body through the pipeline through a main pipe and is injected into a gap between the shaft and the bearing through a pressurized hole in the inner surface of the bearing.
2. The pressurizing holes along the circumferential direction are arranged at the positions, which are vertically below the bearing and contacted with the shaft system, and the distances among the pressurizing holes are gradually sparse along the circumferential direction to the height of the circle center of the bearing by taking the pressurizing holes as a reference.
3. For the intermediate bearing, the uneven distribution of the intervals among the pressurizing holes refers to that: the maximum pressure point is the middle point of the bearing, and the distance between the pressurizing holes is gradually sparse towards two sides by taking the middle point of the bearing as the center.
4. For the bearing, the uneven distribution of the intervals among the pressurizing holes refers to that: the pressure maximum point is located near the left end or the right end, and the pressurizing holes are arranged from the pressure maximum point to the two sides in a gradually sparse trend.
5. The pressure of the pressurizing medium flowing out of each pressurizing hole applied to the shaft is equal.
In order to solve the problems in the prior art, the invention provides a bearing capable of improving the lubricating state of a radial sliding bearing, which mainly adopts a forced lubricating mode, provides a new structural design form, and forcibly generates a targeted lubricating liquid film under the low-speed running working condition of a shafting according to the running state and the pressure distribution condition of the bearing so as to relieve the friction degree of the bearing.
Compared with the prior art, the invention has the following beneficial effects:
(1) the bearing is not changed in overall dimension, holes are formed in the thickness direction of a bearing shell, a lubricating medium with certain pressure is directly injected into a gap between a shaft and the bearing through a pressurizing hole, and an effective dynamic pressure lubricating mode is formed by driving through a rotating shaft system; meanwhile, the open pore position of the pressurizing hole can carry out targeted arrangement on the actual load states of different bearings, thereby realizing better effect.
(2) When the shaft system runs in a fluid dynamic pressure lubrication stage under a rated working condition, the control valve 5-4 can be closed, and the bearing is not different from a conventional bearing. When the rotating speed of the shafting is low, the control valve 5-4 is opened to generate the forced lubrication effect, and meanwhile, the pressurized medium can lift the shafting, so that the state that the load of the bearing is high is relieved.
Drawings
FIG. 1a is a schematic diagram of the variation in spacing between the pressurizing holes with the point of maximum pressure at the bearing center;
FIG. 1b is a cross-sectional view A-A of FIG. 1 a;
FIG. 1C is a cross-sectional view C-C of FIG. 1 a;
FIG. 2a is a schematic diagram of the variation in spacing between the pressurizing holes when the point of maximum pressure is not at the center of the bearing;
FIG. 2b is a cross-sectional view A-A of FIG. 2 a;
FIG. 2C is a cross-sectional view C-C of FIG. 2 a;
FIG. 3 is a general schematic including a pressure servo;
FIG. 4 is a schematic diagram showing the distribution of the liquid film pressure along the length of the bearing with the point of maximum pressure at the center of the bearing;
FIG. 5 is a schematic diagram showing the distribution of the liquid film pressure along the length of the bearing when the pressure maximum point is not at the center of the bearing;
fig. 6a to 6f are the pressure distributions obtained by model calculations, wherein fig. 6a is the original bearing without bore (Pmax 12.9 Mpa); fig. 6b is a model in the patent document entitled "water lubricated hydrostatic stern bearing for marine vessel" (Pmax 7.65 Mpa); fig. 6c is a model of the present invention with the pressure maximum point at the bearing center (Pmax ═ 3.1 MPa); fig. 6d is the original bearing without the bore (Pmax 38.8 Mpa); fig. 6e is a model in the patent document entitled "water lubricated hydrostatic stern bearing for marine vessel" (Pmax 30.6 Mpa); fig. 6f is a model when the maximum pressure point of the present invention is not at the bearing center (Pmax ═ 6.21 MPa).
Detailed Description
The invention is described in more detail below by way of example with reference to the accompanying drawings.
The radial sliding bearing in a low-speed heavy-load environment mainly comprises the following two parts: the bearing body is connected with the pressure servo mechanism through a pipeline. The bearing can be used for water lubrication and oil lubrication, the pressurizing aperture on the bearing can be selected according to the inner diameter size of the shaft hole, and reasonable initial pressure of a pressure servo mechanism is set according to the operation condition of a shaft system, so that forced lubrication of the bearing is realized.
With reference to fig. 1a to 1c, 2a to 2c and 3, the bearing body 1 is axially provided with a pressurizing hole 2, a pressurizing hole 3 and a main oil wiping pipe 4 inside the bearing body. The wear area of the shaft 11 and the bearing is mainly the lower surface of the bearing, and thus the pressurizing holes are mainly concentrated in this area. The pressurizing holes are converged in the manifold 4 through communicating holes in the bearing, and the manifold 4 and the pressurizing holes 2 and 3 on the inner surface of the bearing are ensured to be the only inlets and outlets for pressurizing media and the outside. If the bearing is expanded in the circumferential direction, the arrangement of the pressurizing holes approximates an M × N grid.
The distance between the pressurizing holes is not uniform and accords with the pressure distribution form of the liquid film, and the variation trend of the axially distributed distance between the pressurizing holes meets the axial coordinate
(bearing length L, diameter D).
The positions of the axial pressure holes 2 and the circumferential pressure holes 3 may be defined according to the actual bearing load region. For example, the pressurized holes in the axial direction of the bearing are not uniformly distributed, as shown by L1, L2, L3 and L4 in FIG. 1c, i.e., the hole spacing varies according to the load conditions, and the holes are slightly densely opened near the region with larger load, i.e., L4 is smaller than L3 and smaller than L2 and smaller than L1. The pressurizing holes in the circumferential direction of the bearing are not uniformly distributed, as shown by theta 1, theta 2, theta 3 and theta 4 in fig. 1b, namely, the hole intervals are gradually sparse, and the holes are slightly dense close to the area with larger load, namely, theta 1 is smaller than theta 2 and smaller than theta 3 and smaller than theta 4.
The axial pressurizing holes 2 can be arranged according to the positions shown in fig. 1 a-1 c and fig. 2 a-2 c, and for the middle bearing, if the point with the maximum pressure is the middle point of the bearing, the distance between the shaft holes gradually becomes sparse from the middle point of the bearing to the two sides, as shown in fig. 1 a-1 c. If the shaft system is inclined, the pressure maximum point usually appears at a position closer to the left end or the right end, and the pressurizing holes are also arranged towards two sides in a gradually sparse trend from the maximum pressure point, as shown in fig. 2 a-2 c.
The pressure servo mechanism 5 is formed by connecting a pipeline 5-1, a pump 5-2, a control system 5-3 and a control valve 5-4. The rotating speed sensor 10 detects that the shaft system is in a low-speed running condition, triggers the control system 5-3 and opens the control valve 5-4, instructs the pump 5-2 to work, and injects a pressurized medium into the bearing body 1 through the pipeline 5-1 and the manifold 4, so that the pressurized medium is injected into a gap between the shaft and the bearing through a pressurized hole in the inner surface of the bearing. It is possible to make water-lubricated bearings, oil-lubricated bearings or liquid film-lubricated bearings.
In order to verify the effect of the invention, a model in a patent document entitled "water-lubricated hydrostatic stern bearing for ship" is taken as an example, and further effect comparison is performed on a forced lubrication bearing with distributed pores.
When the rotational speed of the shaft system decreases to a certain limit, the control system 5-3 is activated, the control valve 5-4 is opened, the pump 5-2 is operated, the lubricating medium in the pipe is pressurized and kept at a constant pressure, and the pressurized medium is injected into the bearing manifold 4 via the pipe 5-1, as shown in fig. 3.
The pressurized medium injected into the main pipe 4 flows out to the inner surface of the bearing along the inner pipelines of the bearing body, namely the axial pressurized hole 2 and the circumferential pressurized hole 3, and the pressurized medium is brought into a gap between the shaft and the bearing through the rotating shaft system, so that the lubricating state of the shaft system is improved.
The position of the opening of the pressurized hole inside the bearing depends on the bearing load distribution, taking the middle bearing as an example, the maximum load of the middle bearing is generated at the middle point of the bearing, the pressure distribution satisfies the cubic polynomial of the length x,
is a dimensionless lengthwise coordinate, as shown in fig. 4, so that the positions of the openings can be selected from the positions indicated by the arrows in the figure, and the calculated pressure distribution is shown in fig. 6 a-6 c.
For the traditional bearing result, the model in the patent document named as the water lubrication hydrostatic stern bearing for ships can reduce the maximum liquid film pressure by 40%, and the model can reduce the maximum liquid film pressure by 75%, so that the liquid film pressure is reduced greatly, the bearing friction is relieved, and the application effect is good.
Under some special conditions, the shafting runs in an inclined state, the position of the maximum pressure point of the bearing deviates to two ends, and the pressure distribution meets the requirement
(the bearing length is L) is a dimensionless longitudinal coordinate. As shown in FIG. 5, the position of the opening can be selected from the positions indicated by the arrows in the figure. As described above, the pitch of the openings varies as follows: sparse-dense-sparse (from head to tail), and the density degree depends on the use environment of the bearing. Meanwhile, the bore diameter and the water pressure of the pressurizing hole on the bearing also need to be preset according to the bearing load, and the calculated pressure distribution is shown in fig. 6 e-6 f.
For the traditional bearing result, the model in the patent document entitled "water lubrication hydrostatic stern bearing for ship" can reduce the maximum liquid film pressure by 22%, the model of the invention can reduce the maximum liquid film pressure by 84%, and meanwhile, the bearing liquid film pressure is more uniform than the former two structural forms.
Experimental verification shows that the invention really enables the liquid film pressure to be greatly reduced and the reduction amplitude to be improved to over 75 percent, and enables the bearing pressure to be more uniformly distributed, and the invention can effectively relieve the friction load of the bearing.
Claims (5)
1. The utility model provides a force-feed lubrication bearing with distributed aperture, it has house steward to open at the bearing body inside, characterized by: the bearing body is provided with pressurizing holes leading to the inner surface of the bearing body along the axial direction and the circumferential direction, all the pressurizing holes are converged in a main pipe inside the bearing body, the main pipe is connected with a pressure servo mechanism through a pipeline, the bearing body is expanded along the circumferential direction, the pressurizing holes are in an MXN grid, the distances among the pressurizing holes along the axial direction and the circumferential direction are unevenly distributed, and the distance among the pressurizing holes close to the maximum pressure point is gradually reduced; the pressurizing holes along the circumferential direction are arranged at the position, which is in contact with the shafting, at the lowest part of the bearing, and the distance between the pressurizing holes is gradually sparse along the circumferential direction to the height of the circle center of the bearing by taking the pressurizing holes as a reference.
2. A force-lubricated bearing with distributed porosity as claimed in claim 1, wherein: the pressure servo mechanism is formed by connecting a pipeline, a pump, a control valve and a control system, the control system is triggered, the control valve is opened and the pump is instructed to work under the condition that the shaft system runs at a low speed, a pressurized medium is injected into the bearing body through the pipeline through a main pipe and is injected into a gap between the shaft and the bearing through a pressurized hole in the inner surface of the bearing.
3. A force-lubricated bearing with distributed porosity as claimed in claim 1, wherein: for the intermediate bearing, the uneven distribution of the intervals among the pressurizing holes refers to that: the maximum pressure point is the middle point of the bearing, and the distance between the pressurizing holes is gradually sparse towards two sides by taking the middle point of the bearing as the center.
4. A force-lubricated bearing with distributed porosity as claimed in claim 1, wherein: for the bearing with the inclined shaft system, the uneven distribution of the intervals among the pressurizing holes refers to that: the pressure maximum point is located near the left end or the right end, and the pressurizing holes are arranged from the pressure maximum point to the two sides in a gradually sparse trend.
5. A force-lubricated bearing according to any one of claims 1 to 4 having distributed porosity, wherein: the pressure of the pressurizing medium flowing out of each pressurizing hole applied to the shaft is equal.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010420796.1A CN111637161B (en) | 2020-05-18 | 2020-05-18 | Forced lubrication bearing with distributed pores |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010420796.1A CN111637161B (en) | 2020-05-18 | 2020-05-18 | Forced lubrication bearing with distributed pores |
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| CN111637161A CN111637161A (en) | 2020-09-08 |
| CN111637161B true CN111637161B (en) | 2021-11-09 |
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| CN117085378B (en) * | 2023-10-19 | 2024-01-02 | 烟台核信环保设备有限公司 | Improved plastic filter plate and vertical filter press |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| SE416075B (en) * | 1977-09-01 | 1980-11-24 | Skf Ab | DEVICE FOR MAINTENANCE OF REQUIRED LIQUID PRINTING IN A HYDROSTATIC STOCK |
| CN102788088A (en) * | 2012-07-25 | 2012-11-21 | 青州市溢鑫包装材料有限公司 | Self-adaptive variable working condition cylindrical spherical surface bearing system |
| JP2014035054A (en) * | 2012-08-10 | 2014-02-24 | Oiles Ind Co Ltd | Static pressure gas bearing unit |
| CN103075425A (en) * | 2012-08-27 | 2013-05-01 | 浙江富春江水电设备股份有限公司 | Radial sliding bearing |
| CN203098574U (en) * | 2012-09-03 | 2013-07-31 | 中国工程物理研究院总体工程研究所 | Large precise rotary table air floatation component |
| CN106979223A (en) * | 2017-03-27 | 2017-07-25 | 哈尔滨工程大学 | A kind of rubber shaft bearing for low-speed heave-load environment |
| CN110030266A (en) * | 2019-03-27 | 2019-07-19 | 浙江工业大学 | A kind of aerostatic bearing gas film pressure vector control apparatus |
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