CN108194498A - With the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding - Google Patents
With the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding Download PDFInfo
- Publication number
- CN108194498A CN108194498A CN201711398786.7A CN201711398786A CN108194498A CN 108194498 A CN108194498 A CN 108194498A CN 201711398786 A CN201711398786 A CN 201711398786A CN 108194498 A CN108194498 A CN 108194498A
- Authority
- CN
- China
- Prior art keywords
- bearing
- plane
- fixed bush
- lubricating oil
- bush segment
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
The present invention relates to a kind of special-shaped clinoplain fixed bush segment thrust slide bearings with interface sliding, and including one piece of fixed bush segment and one piece of exercise stress, the value range of the angle theta between fixed bush segment working surface and exercise stress working surface is：1.0×10‑6°≤θ≤1.0×10‑3°, the wedge gap of diverging is formed between fixed bush segment and exercise stress, the exercise stress direction of motion is that the big end of this wedge gap is directed toward from the small end of this wedge gap；Lubricating oil is full of in the gap of this two plate.The working surface of bearing inlets area fixed bush segment is the coating surface for hating oil, and lubricating oil film slides on this surface；Remaining working surface of bearing is the surface of oleophylic, and lubricating oil film does not slide on these surfaces.Bearing of the present invention has certain bearing capacity and relatively low friction coefficient, has significant antifriction and energy-saving effect, is used as bearing part under specific occasion in mechanical equipment.
Description
Technical field
It is specifically a kind of to be pushed away with the special-shaped clinoplain fixed bush segment of interface sliding the present invention relates to field of bearings
Power sliding bearing.
Background technology
Bearing is the important mechanical part for supporting axial workpiece.Mainly it is divided to two kinds of sliding bearing and rolling bearing.It is right
There are following main performance requirements in bearing：Support accuracy, support stiffness, low-friction coefficient and wear-resistant.This requires bearing is
A kind of very accurate mechanical part, also requires it to have sufficiently large bearing capacity.For the antifriction reached and wear-resisting property, go back
Need bearing that there is preferable greasy property.It is developed so far, although bearing technology comparative maturity, establishes in traditional lubrication
In theoretical foundation.At present, 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 two kinds of mixed film friction sliding bearing and fluid lubrication sliding bearing.The former
Lubrication is realized by boundary adsorbed film and hydrodynamic effect, for low speed, underloading and inessential occasion；The latter relies on fluid film
Realize lubrication, for important events, application is more extensive.Fluid lubrication sliding bearing is the main body of sliding bearing, is divided into as stream
Two kinds of body hydrodynamic lubrication sliding bearing and hydrostatic lubrication sliding bearing.Hydrostatic lubrication sliding bearing is by extraneous hydraulic pressure
System fuel feeding by oil lift load, is lubricated by hydraulic oil, and the accuracy of manufacture is high, structure is more complicated, cost is higher, 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, have the advantages that structure compared with it is simple, cost is relatively low, better performances, be a kind of application it is more extensive with
Common sliding bearing.It is divided into as hydrldynamic pressure lubrication radial plain bearing and hydrldynamic pressure lubrication thrust slide bearing two
Kind., for supporting radial load, the latter is used to support axial load for the former.Existing main fluid hydrodynamic lubrication thrust introduced below
Sliding bearing type and its feature.
First, clinoplain segmental bearing, this bearing are as shown in Figure 1.It is by between the convergence formed between upper and lower two surface
Hydrodynamic effect is realized in relative motion between gap and the two surfaces, so as to fulfill lubrication.This bearing has larger carrying energy
Power has preferable antifriction and wear-resisting property.
This bearing is divided into two kinds, it is a kind of be upper and lower surface cannot around the fixed bush segment bearing that fulcrum rotates,
Another kind is the tilting pad bearing that one of surface can be rotated around fulcrum.Under good design, tilting pad bearing is than solid
Determining segmental bearing has the bearing capacity of bigger.
2nd, zigzag segmental bearing, this bearing are as shown in Figure 2.Its work and lubrication mechanism is same as above a kind of bearing.
Its bearing capacity is more much lower than a kind of upper bearing under the same terms.
3rd, ramp platform segmental bearing, this bearing are as shown in Figure 3.Its work and lubrication mechanism is same as above two kinds of bearings.
Its maximum bearing capacity is higher by 20% than the maximum bearing capacity of clinoplain fixed bush segment bearing under identical operating mode.
4th, Rayleigh ladder bearing, this bearing are as shown in Figure 4.Its same spherical bearing of work and lubrication mechanism.Compared to
Three kinds of front bearing, its maximum bearing capacity highest under identical operating mode, than the maximum carrying of clinoplain fixed bush segment bearing
Amount is higher by 28%.
According to conventional fluid lubrication theory, traditional bearing shown in Fig. 1-Fig. 4 all relies on the convergence formed between two surfaces of solids
Wedge gap, under moving surface drive, lubricating oil is seen in from the big section of convergent wedge-shaped gap, is taken out of from its small bore
Come, so as to which lubricating oil be made to be squeezed in convergent wedge-shaped gap and then generate oil pressure, lubricating oil film just has bearing capacity, from
And form hydrldynamic pressure lubrication bearing.According to conventional fluid lubrication theory, in the diverging wedge gap formed between two surfaces of solids
Hydrldynamic pressure lubrication oil film is not likely to form, at this moment is impossible to form bearing.Because at this time under moving surface drive,
The small bore of lubricating oil from diverging wedge gap is seen in, and is brought out from its big section, and such lubricating oil is in diverging wedge
It would not be squeezed in shape gap, would not also generate oil pressure, not have bearing capacity, it is impossible to form lubricating oil film.
Invention content
The object of the present invention is to provide a kind of special-shaped clinoplain fixed bush segment thrust slide bearings with interface sliding.
It is runed counter to conventional fluid lubrication theory, the wedge gap of diverging is formed between this two contact surface of bearing.Incline with tradition shown in Fig. 1
Tapered plane fixed bush segment thrust slide bearing is on the contrary, the surface gap in this bearing inlets area is less than between the surface of its outlet area
Gap.According to conventional fluid lubrication theory, this bearing should be invalid, because lubricating oil is from small section of diverging wedge gap
Face is seen in, and is brought out from its big section, and lubricating oil is not extruded in such gap, cannot also form oil
Pressure, does not have bearing capacity.But if the stationary contact surface in this bearing inlets area is with weaker physical absorption ability
Hate oil coating surface and lubricating oil film made to generate sliding on the stationary contact surface in bearing inlets area, lubricating oil film is in bearing
Remaining surface on do not slide, due to sliding of the lubricating oil film on this bearing inlets area stationary contact surface, moving
Surface flows into this bearing inlets area small bore flow of lubrication under driving is more than the outflow big section in bearing outlet area instead
Flow of lubrication so that lubricating oil can also be squeezed in such diverging wedge gap and then generate oil pressure, moisten
Lubricating oil film just has bearing capacity.Thus form the signified special-shaped clinoplain fixed bush segment thrust slide bearing of the present invention.
Under the wedge gap for the diverging that the present invention abstains from traditional bearing, only with interface sliding technology, it is achieved that tool
Have the special-shaped clinoplain fixed bush segment thrust slide bearing of certain bearing capacity, technically, the present invention have it is prominent into
Step and creativeness.Bearing of the present invention has the advantages that manufacture is easy, of simple structure and low cost.
The present invention technical solution be：
A kind of special-shaped clinoplain fixed bush segment thrust slide bearing with interface sliding, such as Fig. 5, including one piece of fixation
Tile fragment (1), fixed bush segment (1) working surface include plane A (2) and plane C (6), and plane A (2) is to hate oil coating surface, plane
C (6) is the oleophylic coating surface of fixed bush segment (1) or the oleophylic natural surface of fixed bush segment (1)；It is another to have one piece there is plane
The exercise stress (4) of B (3), plane B (3) are that the oleophylic natural surface of exercise stress (4) or the oleophylic of exercise stress (4) apply
Layer surface.Exercise stress (4) is made to be matched with fixed bush segment (1), the plane A of inclination angle, that is, fixed bush segment (1) of fixed bush segment (1)
(2) angle between the plane B of exercise stress (4) (3) is θ, and the value range of θ is：1.0×10-6°≤θ≤1.0×10-3°.Wedge gap is formed between fixed bush segment (1) and exercise stress (4), exercise stress (4) is relative to fixed bush segment (1)
The direction of motion be that the big end of this wedge gap is directed toward by the small end of this wedge gap, full of profit in this wedge gap
Lubricating oil (5), lubricating oil (5) film thickness is h at gap width, that is, bearing inlets at the small end of this wedge gapi, the present invention claims：
In this way, lubricating oil (5) film just generates sliding on plane A (2), here,τsaIt is lubricating oil
(5) interface shear strength between plane A (2), u are movement velocity of the exercise stress (4) relative to fixed bush segment (1), and η is profit
Dynamic viscosity when lubricating oil (5) works, Ho=ho/hi, hoFor lubricating oil at bearing outlet (5) film thickness (see Fig. 5), H1=h1/
hi, h1For inlet region in plane A (2) and plane C (6) boundary, that is, bearing and outlet area boundary lubricating oil (5) film thickness (see
Fig. 5).Lubricating oil (5) film slides on plane A (2), and lubricating oil (5) film does not slide on plane B (3) and plane C (6), this
Sample is formed the special-shaped clinoplain fixed bush segment thrust slide bearing of meaning of the invention.The optimal operating condition of bearing of the present invention
It is：Ψ=l2/l1=0.5, here, l1For the width of plane A (2), l2Width for plane C (6)；On this condition, this axis
It holds with maximum load-carrying capacity.
Further, the plane A (2) of fixed bush segment (1) is fluororine-carbon coating surface, and the plane C (6) of fixed bush segment (1) is
Coating of titanium dioxide surface, the plane B (3) of exercise stress (4) is coating of titanium dioxide surface.
The beneficial effects of the invention are as follows：
The present invention designs a kind of special-shaped clinoplain fixed bush segment with interface sliding technology using surface coating method
Thrust slide bearing.Bearing of the present invention is suitable for the occasion that bearing inlets area surface gap is less than bearing outlet area surface gap,
This is that conventional bevel plane fixed bush segment thrust slide bearing is not achieved.Bearing of the present invention has considerable bearing capacity, tool
There are good lubricating oil film and relatively low friction co-efficient value, preferable anti-friction wear-resistant and energy-saving effect can be played, in mechanical equipment
On be used as bearing part.
The present invention has the following advantages：
(1) bearing of the present invention is suitable for the occasion that bearing inlets area surface gap is less than bearing outlet area surface gap.
(2) bearing of the present invention contains good lubricating oil film, has good antifriction, energy-efficient performance, has certain carrying energy
Power.
(3) bearing arrangement of the present invention is simple, and manufacture is easy, of low cost.
Description of the drawings
Fig. 1 is the structure diagram of existing clinoplain segmental bearing；
Fig. 2 is the structure diagram of existing zigzag segmental bearing；
Fig. 3 is the structure diagram of existing ramp platform segmental bearing；
Fig. 4 is the structure diagram of existing Rayleigh ladder bearing；
Fig. 5 is structure of the embodiment of the present invention with the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding
Schematic diagram；
Fig. 6 is dimensionless lubricating oil (5) film pressure distribution map in the different θ lower bearings in the embodiment of the present invention；
Fig. 7 is the dimensionless bearing capacity (W) of difference θ lower bearings in the embodiment of the present invention with the change curve of Ψ；
Fig. 8 be difference θ lower bearings in the embodiment of the present invention dimensionless bearing capacity (W) withChange curve；
Fig. 9 is the friction coefficient f at the fixed bush segment (1) of middle (center) bearing of the embodiment of the present invention under different θ valuesaValue figure；
Figure 10 is the friction coefficient f at the exercise stress (4) of middle (center) bearing of the embodiment of the present invention under different θ valuesbValue figure.
Wherein, u is movement velocity of the exercise stress relative to fixed bush segment, and w is the bearing of unit contact length upper bearing (metal)
Load, hiFor lubricating oil at bearing inlets (5) film thickness, hoFor lubricating oil at bearing outlet (5) film thickness, h1For plane A (2)
With inlet region in plane C (6) boundary, that is, bearing and outlet area boundary lubricating oil (5) film thickness, l1Width for plane A (2)
Degree, l2For the width of plane C (6), θ is the plane A (2) and exercise stress of inclination angle, that is, fixed bush segment (1) of fixed bush segment (1)
(4) the angle between plane B (3)；Full of lubricating oil in gap between two plates, lubricating oil (5) film is on plane A (2)
Sliding, lubricating oil (5) film do not slide on plane B (3) and plane C (6).
In Fig. 5：1- fixed bush segments, 2- planes A, 3- plane B, 4- exercise stress, 5- lubricating oil, 6- planes C
Specific embodiment
The preferred embodiment that the invention will now be described in detail with reference to the accompanying drawings.
Embodiment
A kind of special-shaped clinoplain fixed bush segment thrust slide bearing with interface sliding, such as Fig. 5, including one piece of fixation
Tile fragment (1), fixed bush segment (1) working surface include plane A (2) and plane C (6), and plane A (2) is to hate oil coating surface, plane
C (6) is the oleophylic coating surface of fixed bush segment (1) or the oleophylic natural surface of fixed bush segment (1)；It is another to have one piece there is plane
The exercise stress (4) of B (3), plane B (3) are that the oleophylic natural surface of exercise stress (4) or the oleophylic of exercise stress (4) apply
Layer surface.Exercise stress (4) is made to be matched with fixed bush segment (1), the plane A of inclination angle, that is, fixed bush segment (1) of fixed bush segment (1)
(2) angle between the plane B of exercise stress (4) (3) is θ, and the value range of θ is：1.0×10-6°≤θ≤1.0×10-3°.Wedge gap is formed between fixed bush segment (1) and exercise stress (4), exercise stress (4) is relative to fixed bush segment (1)
The direction of motion be that the big end of this wedge gap is directed toward by the small end of this wedge gap, full of profit in this wedge gap
Lubricating oil (5), lubricating oil (5) film thickness is h at gap width, that is, bearing inlets at the small end of this wedge gapi, the present invention claims：
In this way, lubricating oil (5) film just generates sliding on plane A (2), here,τsaIt is lubricating oil
(5) interface shear strength between plane A (2), u are movement velocity of the exercise stress (4) relative to fixed bush segment (1), and η is profit
Dynamic viscosity when lubricating oil (5) works, Ho=ho/hi, hoFor lubricating oil at bearing outlet (5) film thickness (see Fig. 5), H1=h1/
hi, h1For inlet region in plane A (2) and plane C (6) boundary, that is, bearing and outlet area boundary lubricating oil (5) film thickness (see
Fig. 5).Lubricating oil (5) film slides on plane A (2), and lubricating oil (5) film does not slide on plane B (3) and plane C (6), this
Sample is formed the special-shaped clinoplain fixed bush segment thrust slide bearing of meaning of the invention.The optimal operating condition of bearing of the present invention
It is：Ψ=l2/l1=0.5, here, l1For the width of plane A (2), l2Width for plane C (6)；On this condition, this axis
It holds with maximum load-carrying capacity.
Bearing of the present invention is suitable for the occasion that bearing inlets area surface gap is less than bearing outlet area surface gap, this is to pass
System clinoplain fixed bush segment thrust slide bearing is not achieved.Bearing of the present invention has certain bearing capacity and relatively low rubs
Coefficient is wiped, there is good lubricating oil film, preferable antifriction, energy-saving effect can be played, be used as bearing part on mechanical equipment.
In embodiment, this kind uses the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding, by fixed watt
Block (1) and exercise stress (4) form this bearing, and two boards block is made of various trade mark steel, but are not excluded for using other materials
It is made.This kind is with the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding, lubricating oil (5) film at bearing inlets
Thickness hiIt must satisfy：
In this way, lubricating oil (5) film just generates sliding on plane A (2), here,τsaIt is lubricating oil
(5) interface shear strength between plane A (2), u are movement velocity of the exercise stress (4) relative to fixed bush segment (1), and η is profit
Dynamic viscosity when lubricating oil (5) works, Ho=ho/hi, hoFor lubricating oil at bearing outlet (5) film thickness (see Fig. 5), H1=h1/
hi, h1For inlet region in plane A (2) and plane C (6) boundary, that is, bearing and outlet area boundary lubricating oil (5) film thickness (see
Fig. 5).Exercise stress (4) is slided with speed u relative to fixed bush segment (1), and the direction of speed u is the plane by fixed bush segment (1)
Plane C (6) one end that fixed bush segment (1) is directed toward in A (2) one end is to be directed toward wedge gap by the small end of wedge gap between bearing surface
Big end, such as Fig. 5.Lubricating oil (5) film slides on plane A (2), and lubricating oil (5) film is equal on plane B (3) and plane C (6)
It does not slide, plane A (2) is to hate oil coating surface, and plane C (6) is the oleophylic coating surface or fixed bush segment of fixed bush segment (1)
(1) oleophylic natural surface, plane B (3) are that the oleophylic natural surface of exercise stress (4) or the oleophylic of exercise stress (4) apply
Layer surface.
Fig. 5 provides the structure diagram of embodiment bearing.In Fig. 5, u is exercise stress (4) relative to fixed bush segment (1)
Movement velocity, load of the w for the bearing of unit contact length upper bearing (metal), hiFor lubricating oil at bearing inlets (5) film thickness, hoFor axis
Hold exit lubricating oil (5) film thickness, h1For inlet region and outlet area side in plane A (2) and plane C (6) boundary, that is, bearing
Lubricating oil (5) film thickness, l at boundary1For the width of plane A (2), l2For the width of plane C (6), θ is the inclination angle of fixed bush segment (1)
That is the angle between the plane A (2) of fixed bush segment (1) and the plane B (3) of exercise stress (4)；Lubricating oil (5) film is in plane A
(2) it is slid on, lubricating oil (5) film does not slide on plane B (3) and plane C (6)；Full of profit in gap between two plates
Lubricating oil (5), plane A (2) are to hate oil coating surface, and plane C (6) is the oleophylic coating surface of fixed bush segment (1) or fixation watt
The oleophylic natural surface of block (1), plane B (3) are the oleophylic natural surface of exercise stress (4) or the oleophylic of exercise stress (4)
Coating surface.
Compared with conventional fluid hydrodynamic lubrication clinoplain fixed bush segment thrust slide bearing shown in FIG. 1, axis of the present invention
Hold has substantial variations in structure, it uses the wedge gap dissipated between bearing surface, breaches the forbidden zone of conventional lubrication technology,
Lubricating oil film lubrication is realized, there is certain bearing capacity and relatively low friction coefficient.Bearing mnanufacture of the present invention is easy, cost
It is cheap, there is good lubrication, antifriction, energy-efficient performance, suitable for specific occasion.Therefore, the technical advantage of bearing of the present invention and
Application value is fairly obvious.
In embodiment, exercise stress (4) and fixed bush segment (1) are steel manufacture, and the plane A (2) of fixed bush segment (1) is
(hating oil) fluororine-carbon coating surface, the plane C (6) of fixed bush segment (1) are (oleophylic) coating of titanium dioxide surface, exercise stress
(4) plane B (3) is (oleophylic) coating of titanium dioxide surface, and lubricating oil (5) is domestic No. 30 machine oil, and lubricating oil (5) works
When dynamic viscosity be η=0.01Pas, the movement velocity of exercise stress (4) is u=200m/s, hi/(l1+l2)=2.5 × 10-4, lubricating oil (5) film thickness h at bearing inletsiIt is 2 μm, interface shear strength during work between lubricating oil (5) and plane A (2)
τsaFor 0.01MPa.During bearing working, lubricating oil (5) film slides on plane A (2), and lubricating oil (5) film is in plane B (3) peace
Face C does not slide on (6)：
(1) work as l1=6mm, l2=2mm, θ=1.0 × 10-6° when, obtain bearing unit length dimension of the present invention carrying
It measures as w=1.02 × 107N/m, the friction coefficient on fixed bush segment (1) are 0.00045, the friction coefficient on exercise stress (4)
It is 0.00043.
(2) work as l1=6mm, l2=2mm, θ=1.0 × 10-5° when, obtain bearing unit length dimension of the present invention carrying
It measures as w=1.018 × 107N/m, the friction coefficient on fixed bush segment (1) are 0.00046, the friction coefficient on exercise stress (4)
It is 0.00044.
(3) work as l1=6mm, l2=2mm, θ=1.0 × 10-4° when, obtain bearing unit length dimension of the present invention carrying
It measures as w=1.01 × 107N/m, the friction coefficient on fixed bush segment (1) are 0.00047, the friction coefficient on exercise stress (4)
It is 0.00045.
(4) work as l1=6mm, l2=2mm, θ=1.0 × 10-3° when, obtain bearing unit length dimension of the present invention carrying
It measures as w=8.82 × 106N/m, the friction coefficient on fixed bush segment (1) are 0.00049, the friction coefficient on exercise stress (4)
It is 0.00047.
Find out from embodiment, bearing of the present invention belongs to a kind of special-shaped clinoplain fixed bush segment thrust slide bearing, it enters
The bearing surface gap of mouth region is less than the bearing surface gap of its outlet area；Bearing of the present invention have certain bearing capacity and
Relatively low friction coefficient has good antifriction, energy-efficient performance, applied on mechanical equipment, is competent at specific workplace, solves
The indeterminable technical problem of traditional bearing of having determined.
The principle of the invention is described as follows：
It is theoretical according to the interface sliding established before, in the bearing designed in the present invention, since lubricating oil (5) film is in fixation
It slides and is not slid on plane B (3) and plane C (6) on the plane A (2) of tile fragment (1), such as Fig. 5, even if in bearing inlets
In the case of area's surface gap is less than bearing outlet area surface gap, in the case where the movement of exercise stress (4) drives, bearing is flowed into
Lubricating oil (5) flow is more than lubricating oil (5) flow of outflow bearing.In this way, the flow equilibrium condition of the fluid flowing in bearing
It is just broken, constantly accumulation is squeezed to form oil pressure lubricating oil (5) within the bearing.The lubricating oil (5) formed in bearing
Film pressure makes to generate pressure gradient flow (i.e. Poiseuille flowings) in bearing inlets area and outlet area respectively, inlet region and goes out
The pressure gradient flow generated in mouth region respectively reduces lubricating oil (5) flow of inflow bearing, makes the lubricating oil of outflow bearing
(5) flow increases, and lubricating oil (5) total flow of inflow bearing is finally made to be equal to lubricating oil (5) total flow of outflow bearing, so as to
Maintain the flowing continuity of lubricating oil (5) within the bearing.This is to say, since lubricating oil (5) film is in the flat of fixed bush segment (1)
Face A slides and is not slid on plane B (3) and plane C (6) on (2), under the inclination angle theta of suitable fixed bush segment (1), this
Lubricating oil (5) film pressure can be necessarily formed in invention bearing, lubricating oil (5) film pressure of formation makes bearing of the present invention have bearing
The ability of load.Since the interface shear strength between the presence of lubricating oil (5) film and lubricating oil (5) and plane A (2) is relatively low, this
Invention bearing has relatively low friction coefficient, and bearing surface abrasion is extremely slight.Here it is the principles of bearing of the present invention.
Fig. 6, which is provided, works as hi/(l1+l2)=2.5 × 10-4、With Ψ=l2/l1Embodiment of the present invention when=1/3
In different θ lower bearings in dimensionless lubricating oil (5) film pressure distribution.In Fig. 6, X=x/ (l1+l2), P=phi/ (u η), p
It is lubricating oil (5) film (dimension) pressure.As can be seen from Figure 6, as θ reduces, lubricating oil (5) film pressure in bearing of the present invention increases
Greatly.
Fig. 7, which is provided, works as hi/(l1+l2)=2.5 × 10-4WithWhen the embodiment of the present invention in difference θ lower bearings
Dimensionless bearing capacity (W) with Ψ change curve.In Fig. 7, W=w/ (u η), w are the load of unit contact length upper bearing (metal) bearing
Lotus, u be exercise stress (4) relative to fixed bush segment (1) movement velocity, η be lubricating oil (5) work when dynamic viscosity, Ψ
=l2/l1.As can be seen from Figure 7, under other duty parameter the same terms, with the reduction of θ, the bearing capacity of bearing of the present invention increases
Greatly；For given operating mode, there are an optimal Ψ values, and the bearing capacity of bearing of the present invention reaches maximum under the Ψ values,
This optimal Ψ value is hardly influenced by θ angles, is taken as 0.5.
Fig. 8, which is provided, works as hi/(l1+l2)=2.5 × 10-4With Ψ=l2/l1Difference θ lower axles in embodiment of the present invention when=1/3
The dimensionless bearing capacity (W) held withChange curve.In Fig. 8, the definition of W is identical in Fig. 7,τsaThe interface shear strength between lubricating oil (5) and plane A (2), u be exercise stress (4) relative to
The movement velocity of fixed bush segment (1), dynamic viscosity when η is lubricating oil (5) work, hiFor lubricating oil at bearing inlets (5) film
Thickness (see Fig. 5).As can be seen from Figure 8, for given operating mode, withReducing, the bearing capacity of bearing of the present invention linearly increases,
This means that the interface shear strength τ between lubricating oil (5) and plane A (2)saReduction and the more significant lubricating oil that then causes
(5) sliding of the film on plane A (2) increases the bearing capacity of bearing of the present invention, therefrom finds out the lubricating oil that the present invention designs
(5) the beneficial technique effect for the highly significant that glide band of the film on plane A (2) comes.
Fig. 9, which is provided, works as hi/(l1+l2)=2.5 × 10-4With Ψ=l2/l1When=1/3 under difference θ values in the embodiment of the present invention
Friction coefficient f at the fixed bush segment (1) of bearingaValue.In Fig. 9,Definition it is identical in Fig. 8.As can be seen from Figure 9, this hair
Friction co-efficient value at the fixed bush segment (1) of bright bearing is than relatively low, this friction co-efficient value is even lubricated than conventional fluid
The friction co-efficient value of clinoplain fixed bush segment thrust slide bearing is much lower.This show bearing of the present invention have preferable antifriction and
Energy-saving effect.From Fig. 9 it is also seen that withReduce, the friction co-efficient value (f at the fixed bush segment (1) of bearing of the present inventiona) linear
Reduce, it means that the interface shear strength τ between lubricating oil (5) and plane A (2)saReduction and then cause more significant
Sliding of lubricating oil (5) film on plane A (2) makes the friction co-efficient value (f at the fixed bush segment (1) of bearing of the present inventiona) reduce.
Therefrom find out the beneficial of another highly significant that glide band of lubricating oil (5) film of the invention designed on plane A (2) comes
Technique effect reduces bearing friction coefficient.
Figure 10, which is provided, works as hi/(l1+l2)=2.5 × 10-4With Ψ=l2/l1The embodiment of the present invention under difference θ values when=1/3
Friction coefficient f at the exercise stress (4) of middle (center) bearingbValue.In Figure 10,Definition it is identical in Fig. 8.As can be seen from Figure 10,
Friction co-efficient value at the exercise stress (4) of bearing of the present invention is than relatively low, this friction co-efficient value even compares conventional fluid
The friction co-efficient value for lubricating clinoplain fixed bush segment thrust slide bearing is much lower.This shows that bearing of the present invention has and preferably subtracts
It rubs and energy-saving effect.From Figure 10 it is also seen that withReduce, the friction co-efficient value at the exercise stress (4) of bearing of the present invention
(fb) linearly reduce, it means that the interface shear strength τ between lubricating oil (5) and plane A (2)saReduction and then cause
Sliding of more significant lubricating oil (5) film on plane A (2) makes the friction co-efficient value at the exercise stress (4) of bearing of the present invention
(fb) reduce.Another for therefrom finding out that glide band of lubricating oil (5) film that designs of the present invention on plane A (2) come is very aobvious
The beneficial technique effect write reduces bearing friction coefficient.
Claims (3)
1. a kind of special-shaped clinoplain fixed bush segment thrust slide bearing with interface sliding, including one piece of fixed bush segment (1),
Fixed bush segment (1) working surface includes plane A (2) and plane C (6), separately there is one piece of exercise stress (4) with plane B (3),
Exercise stress (4) is made to be matched with fixed bush segment (1), the plane A (2) of inclination angle, that is, fixed bush segment (1) of fixed bush segment (1) and movement
Angle between the plane B (3) of tablet (4) is θ, and wedge gap is formed between fixed bush segment (1) and exercise stress (4),
Exercise stress (4) is to be directed toward this wedge gap by the small end of this wedge gap relative to the direction of motion of fixed bush segment (1)
Big end, full of lubricating oil (5) in this wedge gap, moisten at gap width, that is, bearing inlets at the small end of this wedge gap
Lubricating oil (5) film thickness is hi, lubricating oil (5) film thickness is h at gap width, that is, bearing outlet at the big end of this wedge gapo, put down
Inlet region and outlet area boundary lubricating oil (5) film thickness are h in face A (2) and plane C (6) boundary, that is, bearing1, feature
It is：The value range of θ is：1.0×10-6°≤θ≤1.0×10-3°, plane A (2) is to hate oil coating surface, and plane C (6) is
The oleophylic coating surface of fixed bush segment (1) or the oleophylic natural surface of fixed bush segment (1), plane B (3) are exercise stress (4)
Oleophylic natural surface or exercise stress (4) oleophylic coating surface, hi、hoAnd h1It must satisfy the following conditional expression：
In this way, lubricating oil (5) film just generates sliding on plane A (2), here,τsaIt is lubricating oil (5)
Interface shear strength between plane A (2), u are movement velocity of the exercise stress (4) relative to fixed bush segment (1), and η is lubrication
Dynamic viscosity during oily (5) work, Ho=ho/hi, H1=h1/hi；Lubricating oil (5) film slides on plane A (2), lubricating oil (5)
Film does not slide on plane B (3) and plane C (6).
2. the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding, feature are used as described in claim 1
It is：This optimal operating condition of bearing is：ψ=l2/l1=0.5, here, l1For the width of plane A (2), l2For plane C (6)
Width；On this condition, this bearing has maximum load-carrying capacity.
3. the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding, feature are used as described in claim 1
It is：The plane A (2) of fixed bush segment (1) is fluororine-carbon coating surface, and the plane C (6) of fixed bush segment (1) is coating of titanium dioxide
Surface, the plane B (3) of exercise stress (4) is coating of titanium dioxide surface.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711398786.7A CN108194498A (en) | 2017-12-09 | 2017-12-09 | With the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711398786.7A CN108194498A (en) | 2017-12-09 | 2017-12-09 | With the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108194498A true CN108194498A (en) | 2018-06-22 |
Family
ID=62583525
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711398786.7A Pending CN108194498A (en) | 2017-12-09 | 2017-12-09 | With the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108194498A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108916213A (en) * | 2018-06-29 | 2018-11-30 | 张美华 | All there is the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding at entire static surface |
| CN109139700A (en) * | 2018-09-20 | 2019-01-04 | 张美华 | All there is the special-shaped ramp platform thrust slide bearing of interface sliding at entire static surface |
| CN109139683A (en) * | 2018-09-05 | 2019-01-04 | 张美华 | With the special-shaped ramp platform thrust slide bearing of physical absorption |
| CN109139699A (en) * | 2018-09-20 | 2019-01-04 | 张美华 | All there is the special-shaped ramp platform thrust slide bearing of interface sliding at entire moving surface and at inlet region static surface |
| CN110030280A (en) * | 2019-04-03 | 2019-07-19 | 张美华 | It is a kind of to prevent the radial plain bearing that oil film slides at axis surface |
| 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 |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101216068A (en) * | 2008-01-18 | 2008-07-09 | 张永斌 | Thrust bearing applying interface adsorption technology |
| CN101265942A (en) * | 2008-04-21 | 2008-09-17 | 淮海工学院 | Thrust bearing applying interface sliding technology |
| CN101398030A (en) * | 2008-11-14 | 2009-04-01 | 淮海工学院 | Anti friction high bearing capacity micro precision bearing |
| CN102606618A (en) * | 2012-04-01 | 2012-07-25 | 张永斌 | Novel energy-saving tilting-pad thrust slide bearing |
| CN107061501A (en) * | 2017-06-06 | 2017-08-18 | 袁虹娣 | The miniature ladder bearing of abnormity |
| CN107228120A (en) * | 2017-06-19 | 2017-10-03 | 袁虹娣 | New energy-conservation ramp platform thrust slide bearing |
-
2017
- 2017-12-09 CN CN201711398786.7A patent/CN108194498A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101216068A (en) * | 2008-01-18 | 2008-07-09 | 张永斌 | Thrust bearing applying interface adsorption technology |
| CN101265942A (en) * | 2008-04-21 | 2008-09-17 | 淮海工学院 | Thrust bearing applying interface sliding technology |
| CN101398030A (en) * | 2008-11-14 | 2009-04-01 | 淮海工学院 | Anti friction high bearing capacity micro precision bearing |
| CN102606618A (en) * | 2012-04-01 | 2012-07-25 | 张永斌 | Novel energy-saving tilting-pad thrust slide bearing |
| CN107061501A (en) * | 2017-06-06 | 2017-08-18 | 袁虹娣 | The miniature ladder bearing of abnormity |
| CN107228120A (en) * | 2017-06-19 | 2017-10-03 | 袁虹娣 | New energy-conservation ramp platform thrust slide bearing |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108916213A (en) * | 2018-06-29 | 2018-11-30 | 张美华 | All there is the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding at entire static surface |
| CN109139683A (en) * | 2018-09-05 | 2019-01-04 | 张美华 | With the special-shaped ramp platform thrust slide bearing of physical absorption |
| CN109139700A (en) * | 2018-09-20 | 2019-01-04 | 张美华 | All there is the special-shaped ramp platform thrust slide bearing of interface sliding at entire static surface |
| CN109139699A (en) * | 2018-09-20 | 2019-01-04 | 张美华 | All there is the special-shaped ramp platform thrust slide bearing of interface sliding at entire moving surface and at inlet region static surface |
| CN110030280A (en) * | 2019-04-03 | 2019-07-19 | 张美华 | It is a kind of to prevent the radial plain bearing that oil film slides at axis surface |
| 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 |
| CN110043568B (en) * | 2019-04-03 | 2020-12-01 | 张美华 | Antifriction energy-saving centripetal sliding bearing with sliding oil film on surface of bearing hole |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN108194498A (en) | With the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding | |
| CN107228120A (en) | New energy-conservation ramp platform thrust slide bearing | |
| CN108194499A (en) | With the special-shaped ramp platform thrust slide bearing of interface sliding | |
| CN104791381B (en) | The concentric radial plain bearing formed with interface sliding | |
| CN102606618B (en) | Novel energy-saving tilting-pad thrust slide bearing | |
| CN107061501B (en) | Special-shaped miniature step bearing | |
| CN100549446C (en) | A kind of thrust-bearing that uses interface adsorption technology | |
| CN104454980B (en) | Energy-saving radial sliding bearing | |
| CN108488222A (en) | All there is the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding at entire moving surface and at inlet region static surface | |
| CN107869514A (en) | With the special-shaped fixed bush segment thrust slide bearing of physical absorption | |
| CN107956791A (en) | The miniature ramp platform thrust slide bearing of uniform bearing surface small inclination | |
| CN107989897A (en) | The miniature ladder bearing of the non-homogeneous small ladder of bearing surface | |
| CN108916213A (en) | All there is the special-shaped clinoplain fixed bush segment thrust slide bearing of interface sliding at entire static surface | |
| CN109139700A (en) | All there is the special-shaped ramp platform thrust slide bearing of interface sliding at entire static surface | |
| CN109139699A (en) | All there is the special-shaped ramp platform thrust slide bearing of interface sliding at entire moving surface and at inlet region static surface | |
| CN108591246A (en) | With the special-shaped ladder bearing of interface sliding | |
| CN108204406A (en) | All there is the special-shaped ladder bearing of interface sliding at entire moving surface and at inlet region static surface | |
| CN108194500A (en) | Prevent the ladder bearing that at inlet region moving surface and oil film slides at outlet area static surface | |
| CN108006070A (en) | The miniature fixed bush segment thrust slide bearing of uniform bearing surface small inclination | |
| XIA et al. | A SECOND MODE OF ABNORMAL HYDRODYNAMIC WEDGE-PLATFORM THRUST SLIDER BEARING FORMED BY BOUNDARY SLIPPAGE. | |
| CN109139683A (en) | With the special-shaped ramp platform thrust slide bearing of physical absorption | |
| CN107989898A (en) | The miniature ladder bearing of the uniform small ladder of bearing surface | |
| Nakajima et al. | Cutting mechanism of fine ceramics with a single point diamond | |
| CN108591247A (en) | Prevent the ladder bearing that at two surface of inlet region and oil film slides at outlet area moving surface | |
| CN108591267A (en) | All occurs the special-shaped ladder bearing of interface sliding at outlet area static surface and at inlet region static surface |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20180622 |
|
| WD01 | Invention patent application deemed withdrawn after publication |