CN110030280A - It is a kind of to prevent the radial plain bearing that oil film slides at axis surface - Google Patents
It is a kind of to prevent the radial plain bearing that oil film slides at axis surface Download PDFInfo
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- CN110030280A CN110030280A CN201910279402.2A CN201910279402A CN110030280A CN 110030280 A CN110030280 A CN 110030280A CN 201910279402 A CN201910279402 A CN 201910279402A CN 110030280 A CN110030280 A CN 110030280A
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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
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/02—Rigid support of bearing units; Housings, e.g. caps, covers in the case of sliding-contact bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16N—LUBRICATING
- F16N1/00—Constructional modifications of parts of machines or apparatus for the purpose of lubrication
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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
- F16C2202/00—Solid materials defined by their properties
- F16C2202/50—Lubricating properties
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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
- F16C2223/00—Surface treatments; Hardening; Coating
- F16C2223/30—Coating surfaces
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
The radial plain bearing that oil film slides at axis surface is prevented the present invention relates to a kind of, lubricating oil film sliding occurs at the surface for coating oleophylic coating in the whole surface of axis to prevent axis, under specific operating condition, due to preventing the lubricating oil film at axis surface to slide, bearing of the present invention has much bigger bearing capacity and lower coefficient of friction than traditional bearing under identical working condition.Therefore, bearing performance of the present invention is had excellent performance much than traditional bearing.Bearing of the present invention has the advantages that manufacture is easy, of simple structure and low cost, bearing capacity is high, coefficient of friction is low and energy saving.Bearing of the present invention has important application in mechanical equipment.
Description
Technical field
The present invention relates to field of bearings, specifically a kind of to prevent the radial plain bearing that oil film slides at axis surface.
Background technique
Bearing is the important mechanical part for supporting axial workpiece.Mainly it is divided to sliding bearing and two kinds of rolling bearing.It is right
There are a following main performance requirements in bearing: support accuracy, support stiffness, low-friction coefficient and wear-resistant.This requires bearings to be
A kind of very accurate mechanical part, also requires it to have sufficiently large bearing capacity.For the antifriction reached and wear-resisting property, also
Need bearing that there is preferable greasy property.It is developed so far, although bearing technology comparative maturity, establishes in traditional lubrication
In theoretical basis.Currently, rolling bearing and sliding bearing are respectively applied to different occasions, respectively there is its advantage.Due to the present invention relates to
Be sliding bearing, now existing sliding bearing type and technology are summarized as follows:
From lubrication mechanism, sliding bearing is divided into mixed film friction sliding bearing and two kinds of fluid lubrication sliding bearing.The former
Lubrication is realized by boundary adsorbed film and hydrodynamic effect, is used for low speed, underloading and inessential occasion；The latter relies on fluid film
It realizes lubrication, is used for important events, application is more extensive.Fluid lubrication sliding bearing is the main body of sliding bearing, and is divided into stream
Body hydrodynamic lubrication sliding bearing and two kinds of hydrostatic lubrication sliding bearing.Hydrostatic lubrication sliding bearing is by extraneous hydraulic
System fuel feeding leans on oil lift load, is lubricated by hydraulic oil, and the accuracy of manufacture is high, structure is more complex, higher cost, is used for
It is required that support stiffness is big, support accuracy is high and the important events of large carrying capacity.Hydrldynamic pressure lubrication sliding bearing relies on fluid
Dynamic pressure effect realizes lubrication, has the advantages that structure is relatively simple, cost is relatively low, better performances, be a kind of application it is more extensive with
Common sliding bearing.It is divided into hydrldynamic pressure lubrication radial plain bearing and hydrldynamic pressure lubrication thrust slide bearing two again
Kind.The former is for supporting radial load, and the latter is for supporting axial load.Existing main fluid hydrodynamic lubrication introduced below is centripetal
Sliding bearing type and its feature.
One, big L/D ratio radial plain bearing-long bearing
This bearing is as shown in Figure 1.Since draw ratio L/D is larger, this bearing can be processed into unlimited long bearing and can neglect
Slightly fluid side lets out the influence to bearing load carrying capacity.In the bottom-right location of bearing, bearing hole forms convergent wedge gap.Due to
The viscosity of fluid, fluid are adhered on axis, are also adhered on bushing or bearing block.Due to the rotary motion of axis, fluid is by from wedge
The big end section of shape hole is seen in, and is brought out from the small end section of wedge-shaped hole；Fluid is thus by crowded in wedge-shaped hole
Swaging makes lubricating film have the ability for bearing radial load w at lubrication film pressure.This is the working mechanism of this bearing.
Two, small draw ratio radial plain bearing-narrow bearing
This bearing is as shown in Figure 2.Due to draw ratio L/D very little, fluid is serious along the axial leakage (i.e. side is let out) of bearing.
Fluid is squeezed to form lubrication pressure in narrow gap during side is let out, and has lubricating film load bearing
Ability.The wedge gap effect of the hole of this bearing is relatively small, can be ignored.This is the working machine of this bearing
Reason.
Three, Finite Width sliding bearing
This bearing is as shown in Figure 3.Since draw ratio is moderate, bearing forms lubrication membrane pressure by convergent wedge-shaped hole
Power, but the lateral leakage of fluid to lubricate film pressure and bearing load carrying capacity decreases；Draw ratio is smaller, and lateral leakage is got over
Seriously, bearing load carrying capacity reduces bigger.It, should be on the basis of endless bearing load carrying capacity when calculating this bearing load carrying capacity
Consider that fluid side lets out influence and introduces a side related with draw ratio and let out correction factor.
It is steel bearings under the above-mentioned most of occasions of traditional bearing, the working surface of common steel bearings is steel components
Natural surface, this surface does not have the coating of engineer.Generator, steam turbine, large-size machine, compressor, heavy duty machine tools
The use experience of equal heavy mechanical equipments shows under high-speed overload operating condition that the bearing capacity of actually above-mentioned bearing is without tradition
Theory of fluid lubrication design-calculated is so big, these bearings often cannot remain enough because bearing capacity is inadequate in real work
Thick lubricating oil film, and then lead to the ability of losing the job.It should be noted that conventional fluid lubrication theory is not account for lubrication
This phenomenon of sliding of the oil film at bearing surface；But under high-speed overload operating condition, the shear stress at axis surface is very big, usually surpasses
Interface shear strength between lubricating oil and axis surface out, and then lead to sliding of the lubricating oil film at axis surface.This lubricating oil
Sliding of the film at the natural surface of axis declines bearing load carrying capacity sharply, therefore the lubrication at this bearing natural surface
Oil film sliding is very harmful.
Summary of the invention
The radial plain bearing that oil film slides at axis surface is prevented the object of the present invention is to provide a kind of.This is a kind of utilization
Surface coating method coats oleophylic coating in the whole surface of axis to prevent that lubricating oil film sliding occurs at the surface of axis
Radial plain bearing.Under specific operating condition, due to preventing the lubricating oil film at axis surface to slide, identical working condition lower
Invention bearing has much bigger bearing capacity and lower coefficient of friction than traditional bearing.Therefore, bearing performance ratio of the present invention
Traditional bearing is had excellent performance much.
Easy, of simple structure and low cost, bearing capacity is high, coefficient of friction is low and energy saving with manufacturing for bearing of the present invention
The advantages of.Bearing of the present invention has important application in mechanical equipment.
The technical solution of the invention is as follows:
A kind of radial plain bearing for preventing oil film at axis surface from sliding, such as Fig. 4, it includes axis (1) and bearing block (2),
Bearing block (2) is inner bearing hole surface (4), and axis (1) is put into bearing block (2), in axis (1) surface (3) and bearing hole surface (4)
Between have gap, in this gap be full of lubricating oil (5), the center O of axis (1)sTo the center of circle O of bearing hole surface (4)hHave one
A distance, the distance are e, and there are a peripheral velocity u, axis (1) surface in axis (1) surface (3) relative to bearing hole surface (4)
(3) it is oleophylic coating surface, bearing hole surface (4) is oleophylic coating surface, and bearing operating condition satisfies the following conditional expression:
As 0 < ε≤0.69,
As 0.69 < ε < 1,
Here, ε=e/c, e are the center O of axis (1)sTo the center of circle O of bearing hole surface (4)hDistance (see Fig. 4), c=R-r, R
It is the radius of bearing hole surface (4), r is the radius of axis (1), Kτ=τsaC/ (u η), τsaIt is lubricating oil (5) and axis (1) surface (3)
Between interface shear strength, η is the dynamic viscosity of lubricating oil (5), θ0=arccos [(ε+cos φ0)/(1+ε cos φ0)],
φ0It is the cornerite between bearing maximum lubricating oil (5) film pressure position and the entry position (6) of lubricating oil (5), φ0180 ° of <；
In this way, lubricating oil (5) film does not just slide at axis (1) surface (3) and at bearing hole surface (4).
Further, axis (1) surface (3) is coating of titanium dioxide surface, and bearing hole surface (4) is coating of titanium dioxide table
Face.
The beneficial effects of the present invention are:
The present invention uses surface-coating technology, occurs lubricating oil film sliding in radial plain bearing in certain condition range
Axis surface on coating oleophylic coating to improve interface shear strength between this surface and lubricating oil, and then prevent lubricating oil
Sliding of the film on axis surface.There are bearing of the present invention extremely significant advantageous effects to greatly improve bearing load carrying capacity
With significantly reduce bearing friction coefficient, therefore bearing of the present invention have the advantages that bearing capacity height, coefficient of friction it is low and energy saving, have
There is very important application value.
The invention has the following advantages that
(1) bearing of the present invention bearing capacity with higher has good antifriction energy-saving containing good lubricating oil film
Energy.
(2) bearing arrangement of the present invention is simple, and manufacture is easy, low in cost.
Detailed description of the invention
Fig. 1 is big L/D ratio radial plain bearing, i.e. the structural schematic diagram of the long bearing of L/D >=5；
Fig. 2 is small draw ratio radial plain bearing, i.e. the structural schematic diagram of the narrow bearing of L/D≤0.2；
Fig. 3 is Finite Width radial plain bearing, i.e. the structural schematic diagram of the bearing of 0.2 < L/D < 5；
Fig. 4 is the structural schematic diagram of the embodiment of the present invention；
In Fig. 1, Fig. 2, Fig. 3, Fig. 4,1- axis, 2- bearing block, 3- axis (1) surface, 4- bearing hole surface, 5- lubricating oil, 6-
The entry position of lubricating oil (5), the outlet port of 7- lubricating oil (5).
Fig. 5 is bearing dimensionless lubricating oil (5) film pressure (P of the present invention in embodimentconv) distribution and its with identical operating condition
Lower traditional bearing dimensionless lubricating oil (5) film pressure (Pslip) distribution comparison figure；
Fig. 6 is bearing dimensionless bearing capacity (W of the present invention in embodimentconv) and its it is immeasurable with traditional bearing under identical operating condition
Guiding principle bearing capacity (Wslip) comparison figure；
Fig. 7 is coefficient of friction (f at axis (1) surface (3) of bearing of the present invention in embodimentS, conv) value and its with identical work
Coefficient of friction (f at the axis surface of traditional bearing under conditionS, slip) value comparison figure；
Fig. 8 is coefficient of friction (f at bearing hole surface (4) of the invention in embodimentH, conv) value and its under identical operating condition
Coefficient of friction (f at the bearing hole surface of traditional bearingH, slip) value comparison figure.
Specific embodiment
The preferred embodiment that the invention will now be described in detail with reference to the accompanying drawings.
Embodiment
A kind of radial plain bearing for preventing oil film at axis surface from sliding, such as Fig. 4, it includes axis (1) and bearing block (2),
Bearing block (2) is inner bearing hole surface (4), and axis (1) is put into bearing block (2), in axis (1) surface (3) and bearing hole surface (4)
Between have gap, in this gap be full of lubricating oil (5), the center O of axis (1)sTo the center of circle O of bearing hole surface (4)hHave one
A distance, the distance are e, and there are a peripheral velocity u, axis (1) surface in axis (1) surface (3) relative to bearing hole surface (4)
(3) it is oleophylic coating surface, bearing hole surface (4) is oleophylic coating surface, and bearing operating condition satisfies the following conditional expression:
As 0 < ε≤0.69,
As 0.69 < ε < 1,
Here, ε=e/c, e are the center O of axis (1)sTo the center of circle O of bearing hole surface (4)hDistance (see Fig. 4), c=R-r, R
It is the radius of bearing hole surface (4), r is the radius of axis (1), Kτ=τsaC/ (u η), τsaIt is lubricating oil (5) and axis (1) surface (3)
Between interface shear strength, η is the dynamic viscosity of lubricating oil (5), θ0=arccos [(ε+cos φ0)/(1+ε cos φ0)],
φ0It is the cornerite between bearing maximum lubricating oil (5) film pressure position and the entry position (6) of lubricating oil (5), φ0180 ° of <；
In this way, lubricating oil (5) film does not just slide at axis (1) surface (3) and at bearing hole surface (4).Material is thus formed
Signified a kind of radial plain bearing for preventing oil film sliding at axis surface of the invention.
It is of the invention under identical working condition due to preventing the lubricating oil film at axis surface to slide under specific operating condition
Bearing has much bigger bearing capacity and lower coefficient of friction than traditional bearing.Therefore, bearing performance of the present invention is than tradition
Bearing performance is much excellent.Easy, of simple structure and low cost, bearing capacity is high, coefficient of friction with manufacturing for bearing of the present invention
Low and energy saving advantage.
In embodiment, this kind of a kind of radial plain bearing for preventing oil film sliding at axis surface, by axis (1) and bearing block
(2) it forms, axis (1) and bearing block (2) are made of various trade mark steel, but are not excluded for being made using other materials.This kind of one kind
The radial plain bearing that oil film slides at axis surface is prevented, there is a circumference on axis (1) surface (3) relative to bearing hole surface (4)
Linear velocity u, axis (1) surface (3) are oleophylic coating surface, and bearing hole surface (4) is oleophylic coating surface.
Fig. 4 provides the structural schematic diagram of embodiment bearing.In Fig. 4, u: relative to bearing hole surface (4), axis (1) surface
(3) peripheral velocity；wconv: the load that bearing contact unit length of the present invention is born；E: the center O of axis (1)sTo bearing hole
The center of circle O on surface (4)hDistance；R: the radius of bearing hole surface (4)；R: the radius of axis (1)；pConv, max: in bearing of the present invention
Maximum lubricating oil (5) film pressure；φ0: bearing maximum lubricating oil (5) film pressure position and the entry position (6) of lubricating oil (5) it
Between cornerite, φ0180 ° of <；Axis (1) surface (3) is oleophylic coating surface, and bearing hole surface (4) is oleophylic coating surface；?
There is gap between axis (1) surface (3) and bearing hole surface (4), is full of lubricating oil (5) in this gap；Lubricating oil (5) film exists
It is not slid at axis (1) surface (3) and at bearing hole surface (4).
In embodiment, axis (1) and bearing block (2) are steel manufacture, and the radius r of axis (1) is 20mm, and bearing clearance c is
20 μm, relative to bearing hole surface (4), the peripheral velocity u on axis (1) surface (3) is 6m/s, and axis (1) surface (3) is (oleophylic
) coating of titanium dioxide surface, bearing hole surface (4) is coating of titanium dioxide surface, and lubricating oil (5) is domestic No. 30 machine oil,
Lubricating oil dynamic viscosity at an atmospheric pressure and 40 DEG C is η=0.03Pas, between lubricating oil (5) and axis (1) surface (3)
Interface shear strength τsaFor 0.3MPa, bearing operating temperatures are 40 DEG C, and bearing of the present invention moistens in 40 DEG C of work in embodiment
Lubricating oil (5) film does not slide at axis (1) surface (3) and at bearing hole surface (4), and traditional bearing (surface of axis and
Bearing hole surface is the bearing for being not coated by the i.e. natural surface of artificial coating) lubricating oil (5) film exists under identical operating condition
Axis slides on (1):
(1) when eccentricity epsilon=0.05, obtained bearing Load Per Unit Length of the present invention is wconv=1.62 × 105N/
M, coefficient of friction (f at axis (1) surface (3) of bearing of the present inventionS, conv) value is 0.009, at bearing hole surface (4) of the invention
Coefficient of friction (fH, conv) value be 0.009, at this time traditional bearing Load Per Unit Length be wslip=4.5 × 103N/m, traditional axis
Coefficient of friction (f at the axis surface heldS, slip) value is 0.013, coefficient of friction (f at the bearing hole surface of traditional bearingH, slip) value
It is 0.013.
(2) when eccentricity epsilon=0.1, obtained bearing Load Per Unit Length of the present invention is wconv=1.98 × 105N/
M, coefficient of friction (f at axis (1) surface (3) of bearing of the present inventionS, conv) value is 0.005, at bearing hole surface (4) of the invention
Coefficient of friction (fH, conv) value be 0.005, at this time traditional bearing Load Per Unit Length be wslip=7.44 × 103N/m, traditional axis
Coefficient of friction (f at the axis surface heldS, slip) value is 0.007, coefficient of friction (f at the bearing hole surface of traditional bearingH, slip) value
It is 0.007.
(3) when eccentricity epsilon=0.15, obtained bearing Load Per Unit Length of the present invention is wconv=2.85 × 105N/
M, coefficient of friction (f at axis (1) surface (3) of bearing of the present inventionS, conv) value is 0.0035, at bearing hole surface (4) of the invention
Coefficient of friction (fH, conv) value be 0.0035, at this time traditional bearing Load Per Unit Length be wslip=1.0 × 104N/m, traditional axis
Coefficient of friction (f at the axis surface heldS, slip) value is 0.0048, coefficient of friction (f at the bearing hole surface of traditional bearingH, slip) value
It is 0.0048.
(4) when eccentricity epsilon=0.2, obtained bearing Load Per Unit Length of the present invention is wconv=3.59 × 105N/
M, coefficient of friction (f at axis (1) surface (3) of bearing of the present inventionS, conv) value is 0.003, at bearing hole surface (4) of the invention
Coefficient of friction (fH, conv) value be 0.003, at this time traditional bearing Load Per Unit Length be wslip=1.32 × 104N/m, traditional axis
Coefficient of friction (f at the axis surface heldS, slip) value is 0.0039, coefficient of friction (f at the bearing hole surface of traditional bearingH, slip) value
It is 0.0039.
(5) when eccentricity epsilon=0.25, obtained bearing Load Per Unit Length of the present invention is wconv=5.69 × 105N/
M, coefficient of friction (f at axis (1) surface (3) of bearing of the present inventionS, conv) value is 0.0023, at bearing hole surface (4) of the invention
Coefficient of friction (fH, conv) value be 0.0023, at this time traditional bearing Load Per Unit Length be wslip=1.67 × 104N/m, tradition
Coefficient of friction (f at the axis surface of bearingS, slip) value is 0.003, coefficient of friction (f at the bearing hole surface of traditional bearingH, slip)
Value is 0.003.
(6) when eccentricity epsilon=0.3, obtained bearing Load Per Unit Length of the present invention is wconv=6.39 × 105N/
M, coefficient of friction (f at axis (1) surface (3) of bearing of the present inventionS, conv) value is 0.002, at bearing hole surface (4) of the invention
Coefficient of friction (fH, conv) value be 0.002, at this time traditional bearing Load Per Unit Length be wslip=2.1 × 104N/m, traditional axis
Coefficient of friction (f at the axis surface heldS, slip) value is 0.0025, coefficient of friction (f at the bearing hole surface of traditional bearingH, slip) value
It is 0.0025.
(7) when eccentricity epsilon=0.4, obtained bearing Load Per Unit Length of the present invention is wconv=7.17 × 105N/
M, coefficient of friction (f at axis (1) surface (3) of bearing of the present inventionS, conv) value is 0.0018, at bearing hole surface (4) of the invention
Coefficient of friction (fH, conv) value be 0.0018, at this time traditional bearing Load Per Unit Length be wslip=2.64 × 104N/m, tradition
Coefficient of friction (f at the axis surface of bearingS, slip) value is 0.002, coefficient of friction (f at the bearing hole surface of traditional bearingH, slip)
Value is 0.002.
(8) when eccentricity epsilon=0.5, obtained bearing Load Per Unit Length of the present invention is wconv=8.04 × 105N/
M, coefficient of friction (f at axis (1) surface (3) of bearing of the present inventionS, conv) value is 0.0017, at bearing hole surface (4) of the invention
Coefficient of friction (fH, conv) value be 0.0017, at this time traditional bearing Load Per Unit Length be wslip=2.96 × 104N/m, tradition
Coefficient of friction (f at the axis surface of bearingS, slip) value is 0.0018, coefficient of friction (f at the bearing hole surface of traditional bearingH, slip)
Value is 0.0018.
Find out from embodiment, under given operating condition, the bearing capacity of bearing of the present invention is held than traditional bearing under the same terms
Carrying capacity is much bigger, and the coefficient of friction of bearing of the present invention is obviously lower than the coefficient of friction of traditional bearing, and this demonstrate prevent
Lubricating oil (5) film slides the extremely significant beneficial technical effect of bring on axis (1) surface (3) of bearing of the present invention.
The principle of the invention is described as follows:
Such as Fig. 4, for bearing arrangement form shown in the present invention, if using traditional bearing, axis (1) table of bearing
Face (3) and bearing hole surface (4) are natural surface, for the natural surface of steel components, plain oil such as machine oil and this
Interface shear strength between kind natural surface is no more than 0.01MPa at an atmospheric pressure and 40 DEG C.On higher axis (1) surface
(3) relative under the peripheral velocity u and larger bearing load of bearing hole surface (4) as in embodiment peripheral velocity u and
Under bearing load, for plain oil such as machine oil, in the traditional bearing of Fig. 4 structure type, lubricating oil film shear stress absolute value
The interface shear strength that can be greater than at axis surface between axis surface and lubricating oil, so as to cause lubricating oil film on entire axis surface
Sliding.Sliding of the lubricating oil film on axis surface prevent lubricating oil from fully being brought into bearing, so as to cause axis is entered
The flow of the lubricating oil held reduces, and to maintain flowing of the lubricating oil in bearing continuous, flows into the flow of lubrication of bearing
Equal to the flow of lubrication of outflow bearing, the lubricating oil film pressure in bearing must be reduced accordingly, to respectively reduce bearing inlets
The pressure gradient flow (i.e. Poiseuille flowing) of lubricating oil in area and outlet area, to increase the profit for flowing into bearing respectively
Oil flow and the flow of lubrication for reducing outflow bearing, finally maintain flow equilibrium of the lubricating oil in bearing.Here it is
It says, the profit on axis surface occurs at higher peripheral velocity u and larger bearing load for the traditional bearing of Fig. 4 structure type
The sliding of lubricating oil film can be such that the bearing capacity of bearing significantly reduces；For given load, the reduction of this bearing capacity is so that pass
Bearing working unite under lower oil film thickness, and the shear strain rate so that the lubricating oil film in bearing is thinned in lubricating oil film
Increase, so that the value of shearing of bearing surface increases, so that the frictional force of bearing surface and coefficient of friction increase.Conversely,
As representative of the present invention, if sliding of the lubricating oil film on axis (1) surface (3) can be prevented using surface-coating technology,
The bearing capacity of the bearing of Fig. 4 structure type will greatly improve, and the coefficient of friction of the bearing can be then substantially reduced.Here it is
The principle of the present invention.
Fig. 5 gives when eccentricity epsilon=0.25 bearing dimensionless lubricating oil (5) film pressure of the present invention in embodiment
(Pconv) distribution and its with traditional bearing dimensionless lubricating oil (5) film pressure (P under identical operating conditionslip) distribution comparison.Here,
Dimensionless lubricating oil (5) film pressure unified definition are as follows: P=pc2/ (u η r), p are lubricating oil (5) film pressures with dimension in bearing
(unit is Pa), c=R-r, R are the radiuses of bearing hole surface (4), and r is the radius of axis (1), and η is that the power of lubricating oil (5) is viscous
Degree, u is the peripheral velocity relative to bearing hole surface (4), axis (1) surface (3), and subscript " conv " represents bearing of the present invention,
Subscript " slip " represents traditional bearing, and (surface of axis and bearing hole surface are the axis for being not coated by the i.e. natural surface of artificial coating
It holds).As can be seen from Figure 5, lubricating oil (5) film pressure (P under identical working condition, in bearing of the present inventionconv) than in traditional bearing
Lubricating oil (5) film pressure (Pslip) be higher by more than 10 times.This shows that under identical working condition, bearing of the present invention is than traditional axis
It holds with much bigger bearing capacity.
Fig. 6 gives in embodiment bearing dimensionless bearing capacity (W of the present invention under different eccentricity epsilonsconv) and its with it is identical
Traditional bearing dimensionless bearing capacity (W under operating conditionslip) comparison.Here, bearing dimensionless bearing capacity unified definition are as follows: W=wc2/
(uηr2), w is the bearing capacity (unit is N/m) of the contact unit length of bearing, and the definition of c, r, η and u are identical as in Fig. 5,
Subscript " conv " represents bearing of the present invention, and subscript " slip " represents traditional bearing.As can be seen from Figure 6, under identical working condition, this hair
Bearing capacity (the W of bright bearingconv) than the bearing capacity (W of traditional bearingslip) be higher by more than 10 times.This is with shown in fig. 5 consistent, table
The bearing of the present invention under identical working condition, which is illustrated, has the bearing capacity more much bigger than traditional bearing.
Fig. 7 gives in embodiment coefficient of friction (f at axis (1) surface (3) of bearing of the present inventionS, conv) value and its with phase
With coefficient of friction (f at the axis surface of traditional bearing under operating conditionS, slip) value comparison.In Fig. 7, definition and the phase in Fig. 5 of c and r
Together.As can be seen from Figure 7, under identical working condition, especially under lesser eccentricity epsilon value, axis (1) surface of bearing of the present invention
(3) coefficient of friction (f atS, conv) value is than coefficient of friction (f at the axis surface of traditional bearingS, slip) value obviously wants low, this shows this
Invention bearing has significant antifriction and energy-saving effect.
Fig. 8 gives coefficient of friction (f at bearing hole surface (4) of the invention in embodimentH, conv) value and its with identical work
Coefficient of friction (f at the bearing hole surface of traditional bearing under conditionH, slip) value comparison.In Fig. 8, definition and the phase in Fig. 5 of c and r
Together.As can be seen from Figure 8, under identical working condition, especially under lesser eccentricity epsilon value, at bearing hole surface (4) of the invention
Coefficient of friction (fH, conv) value is than coefficient of friction (f at the bearing hole surface of traditional bearingH, slip) value obviously wants low, this shows this hair
Bright bearing has significant antifriction and energy-saving effect.
Claims (2)
1. a kind of prevent the radial plain bearing that oil film slides at axis surface, including axis (1) and bearing block (2), it is characterised in that:
Bearing block (2) is inner bearing hole surface (4), and axis (1) is put into bearing block (2), in axis (1) surface (3) and bearing hole surface (4)
Between have gap, in this gap be full of lubricating oil (5), the center O of axis (1)sTo the center of circle O of bearing hole surface (4)hHave one
A distance, the distance are e, and there are a peripheral velocity u, axis (1) surface in axis (1) surface (3) relative to bearing hole surface (4)
(3) it is oleophylic coating surface, bearing hole surface (4) is oleophylic coating surface, and bearing operating condition satisfies the following conditional expression:
As 0 < ε≤0.69,
As 0.69 < ε < 1,
Here, ε=e/c, c=R-r, R are the radiuses of bearing hole surface (4), and r is the radius of axis (1), Kτ=τsaC/ (u η), τsa
It is the interface shear strength between lubricating oil (5) and axis (1) surface (3), η is the dynamic viscosity of lubricating oil (5), θ0=arccos
[(ε+cosφ0)/(1+εcosφ0)], φ0It is the entry position of bearing maximum lubricating oil (5) film pressure position and lubricating oil (5)
(6) cornerite between, φ0180 ° of <；In this way, lubricating oil (5) film is at axis (1) surface (3) and at bearing hole surface (4) with regard to equal
It does not slide.
2. a kind of radial plain bearing for preventing oil film sliding at axis surface as described in claim 1, it is characterised in that: axis
(1) surface (3) are coating of titanium dioxide surface, and bearing hole surface (4) is coating of titanium dioxide surface.
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| CN108591246A (en) * | 2017-12-09 | 2018-09-28 | 袁虹娣 | With the special-shaped ladder bearing of interface sliding |
| CN110043568A (en) * | 2019-04-03 | 2019-07-23 | 张美华 | The antifriction energy-saving radial plain bearing of oil film sliding at a kind of bearing hole surface |
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|---|---|---|---|---|
| CN104454980A (en) * | 2014-10-22 | 2015-03-25 | 张永斌 | Novel energy-saving radial sliding bearing |
| CN104791381A (en) * | 2015-04-27 | 2015-07-22 | 张永斌 | Concentric centripetal sliding bearing formed by using interface slippage |
| CN104863971A (en) * | 2015-04-27 | 2015-08-26 | 张永斌 | Concentric micro centering slide bearing formed by physical absorption |
| CN108194498A (en) * | 2017-12-09 | 2018-06-22 | 袁虹娣 | With the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding |
| CN108591246A (en) * | 2017-12-09 | 2018-09-28 | 袁虹娣 | With the special-shaped ladder bearing of interface sliding |
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| CN110043568A (en) * | 2019-04-03 | 2019-07-23 | 张美华 | The antifriction energy-saving radial plain bearing of oil film sliding at a kind of bearing hole surface |
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Application publication date: 20190719 |