CN108204406A - All there is the special-shaped ladder bearing of interface sliding at entire moving surface and at inlet region static surface - Google Patents
All there is the special-shaped ladder bearing of interface sliding at entire moving surface and at inlet region static surface Download PDFInfo
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- CN108204406A CN108204406A CN201711500208.XA CN201711500208A CN108204406A CN 108204406 A CN108204406 A CN 108204406A CN 201711500208 A CN201711500208 A CN 201711500208A CN 108204406 A CN108204406 A CN 108204406A
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- plane
- bearing
- lubricating oil
- inactive plate
- exercise stress
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
-
- 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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
The present invention relates to the special-shaped ladder bearing of interface sliding all occur at a kind of entire moving surface and at inlet region static surface, including one piece of inactive plate and one piece of exercise stress, inactive plate working surface is step-like surface, the protrusion working surface of exercise stress and inactive plate is mutually parallel, this two plate interspace of bearing inlets area is less than this two plate interspace of outlet area, full of lubricating oil in this two plate interspace, the exercise stress direction of motion is to be directed toward outlet area from bearing inlets area.Lubricating oil all slides on bearing inlets area inactive plate surface and exercise stress whole surface, and is not slid in bearing remaining surface.Interface shear strength is more than interface shear strength between lubricating oil and inlet region inactive plate surface between lubricating oil and exercise stress surface.Bearing of the present invention has certain bearing capacity and compared with low-friction coefficient, has notable antifriction and energy-saving effect, is used as bearing part under specific occasion in mechanical equipment.
Description
Technical field
The present invention relates to field of bearings, all go out at specifically a kind of entire moving surface and at inlet region static surface
The special-shaped ladder bearing of existing interface sliding.
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 interface sliding all occur at a kind of entire moving surface and at inlet region static surface
Special-shaped ladder bearing.It is runed counter to conventional fluid lubrication theory, the gap of diverging is formed between this two contact surface of bearing.With figure
Traditional ladder bearing shown in 4 is on the contrary, the surface gap in this bearing inlets area is less than the surface gap of its outlet area.According to biography
System theory of fluid lubrication, this bearing should be invalid, because lubricating oil is seen in from the small bore of diverging gap, and from
Its big section is brought out, and lubricating oil is not extruded in such gap, cannot also form oil pressure, does not have carrying
Ability.But if the static surface in this bearing inlets area for weaker physical absorption ability hating oil coating surface and
Lubricating oil film is made to generate sliding in the static surface in bearing inlets area, while lubricating oil film is also in the entire movement of this bearing
Sliding is generated on surface, but the interface shear strength in this bearing between lubricating oil film and moving surface is more than lubricating oil film and enters
Interface shear strength between the static surface of mouth region, and lubricating oil film is in the outlet area static surface of remaining surface, that is, bearing of bearing
On do not slide, due to sliding of the lubricating oil film in this bearing inlets area static surface and entire moving surface, moving
Under surface drives, the outflow heavy in section profit of outlet area will be more than instead by flowing into the flow of lubrication of this bearing inlets area small bore
Oil flow, so that lubricating oil can also be squeezed in such diverging wedge gap and then generate oil pressure, lubricating oil
Film just has bearing capacity.It is thus formed at the signified entire moving surface of the present invention and all occurred at inlet region static surface
The special-shaped ladder bearing of interface sliding.
Under the surface gap for the diverging that the present invention abstains from traditional bearing, only with interface sliding technology, it is achieved that tool
There is the special-shaped ladder bearing of certain bearing capacity, technically, the present invention has prominent progress and creativeness.Bearing of the present invention
Have the advantages that manufacture is easy, of simple structure and low cost, friction coefficient is low and energy saving.
The present invention technical solution be：
All occur the special-shaped ladder bearing of interface sliding at a kind of entire moving surface and at inlet region static surface, such as scheme
5, including one piece of inactive plate (1), the working surface of inactive plate (1) includes plane A (2), plane B (3) and cascaded surface (4),
Plane A (2) and plane B (3) are mutually parallel, and cascaded surface (4) is vertical with plane A (2) and plane B (3) respectively, cascaded surface (4)
Highly i.e. step size is Δ h；The physical adsorption characteristic of plane A (2) and the physical adsorption characteristic of plane B (3) differ, plane
A (2) is to hate oil coating surface, and plane B (3) is the oleophylic natural surface of oleophylic coating surface or inactive plate (1).The present invention
Another to have one piece of exercise stress (6) with plane C (5) (working surface), the physical absorption of the plane C (5) of exercise stress (6) is special
Property is identical everywhere, and plane C (5) is the coating surface on the natural surface or exercise stress (6) of exercise stress (6).Make movement
Tablet (6) is matched with inactive plate (1), and the plane C (5) and the plane A (2) of inactive plate (1) for making exercise stress (6) are mutually flat
Row, full of lubricating oil (7) in the gap between inactive plate (1) and exercise stress (6), the plane C (5) of exercise stress (6) and
The distance between plane A (2) of inactive plate (1) is that bearing inlets area lubricating oil (7) film thickness is hi, definition：ψ=l2/l1,
The present invention claims：Interface shear strength τ between lubricating oil (7) and plane C (5)sbMore than the boundary between lubricating oil (7) and plane A (2)
Face shear strength τsa,AndInterface between lubricating oil (7) and plane B (3)
Shear strength τscMore than the absolute value of the shear stress at plane B (3), i.e.,：In this way, lubricating oil
(7) film just generates sliding on plane A (2) and entire plane C (5), and lubricating oil (7) film does not slide then on plane B (3)；
Here, u is movement velocity of the exercise stress (6) relative to inactive plate (1), and η is dynamic viscosity when lubricating oil (7) works,
λh=ho/hi, hoIt is bearing outlet area lubricating oil (7) film thickness, l1It is the width of the plane A (2) of inactive plate (1), l2It is quiet
The only width of the plane B (3) of plate (1).The direction of motion of exercise stress (6) is plane A (2) one end by inactive plate (1)
It is directed toward plane B (3) one end of inactive plate (1).Material is thus formed at signified entire moving surface of the invention and inlet regions
All occurs the special-shaped ladder bearing of interface sliding at static surface.The optimal operating condition of bearing of the present invention is：ψ=l2/l1=0.6；
On this condition, this bearing has maximum load-carrying capacity.
Further, the plane A (2) of inactive plate (1) is fluororine-carbon coating surface, and the plane B (3) of inactive plate (1) is
Coating of titanium dioxide surface, the plane C (5) of exercise stress (6) is steel components natural surface.
The beneficial effects of the invention are as follows：
The present invention designs a kind of special-shaped ladder bearing with interface sliding technology using surface coating method.The present invention
Bearing is suitable for the occasion that bearing inlets area surface gap is less than bearing outlet area surface gap, this is traditional ladder bearing up to not
It arrives.Bearing of the present invention have certain bearing capacity and relatively low friction coefficient, have good lubricating oil film, can play compared with
Good antifriction energy-saving effect, is used as bearing part on mechanical equipment.
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-saving 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 that all occur the abnormity of interface sliding at the entire moving surface of the embodiment of the present invention and at inlet region static surface
The structure diagram of ladder bearing；
Fig. 6 is lubricating oil (7) film pressure distribution schematic diagram in bearing of the present invention in embodiment；
Fig. 7 is dimensionless lubricating oil (7) film pressure distribution map under different Δ H in bearing of the present invention in embodiment；
Fig. 8 is the dimensionless bearing capacity W of bearing of the present invention under different Δ H in embodiment with the change curve of ψ；
Fig. 9 is the friction coefficient f at the inactive plate (1) of the bearing in the embodiment of the present invention under different U values and Δ H valuesa
Value figure；
Figure 10 is the friction coefficient f at the exercise stress (6) of the bearing in the embodiment of the present invention under different U values and Δ H valuesb
Value figure.
Wherein, u is movement velocity of the exercise stress relative to inactive plate, and w is the bearing of unit contact length upper bearing (metal)
Load, l1The width in width, that is, bearing inlets area of the plane A (2) for inactive plate (1), l2Plane B for inactive plate (1)
(3) width in width, that is, bearing outlet area, step sizes of the Δ h for height, that is, bearing of cascaded surface (4), hiFor bearing inlets
Area's lubricating oil (7) film thickness, hoFor bearing outlet area lubricating oil (7) film thickness；Lubricating oil is full of in gap between two plates,
Lubricating oil (7) film generates sliding on plane A (2) and entire plane C (5), and lubricating oil (7) film does not generate cunning on plane B (3)
It moves.
In Fig. 5：1- inactive plates, 2- planes A, 3- plane B, 4- cascaded surface, 5- planes C, 6- exercise stress, 7- lubricating oil
Specific embodiment
The preferred embodiment that the invention will now be described in detail with reference to the accompanying drawings.
Embodiment
All occur the special-shaped ladder bearing of interface sliding at a kind of entire moving surface and at inlet region static surface, such as scheme
5, including one piece of inactive plate (1), the working surface of inactive plate (1) includes plane A (2), plane B (3) and cascaded surface (4),
Plane A (2) and plane B (3) are mutually parallel, and cascaded surface (4) is vertical with plane A (2) and plane B (3) respectively, cascaded surface (4)
Highly i.e. step size is Δ h；The physical adsorption characteristic of plane A (2) and the physical adsorption characteristic of plane B (3) differ, plane
A (2) is to hate oil coating surface, and plane B (3) is the oleophylic natural surface of oleophylic coating surface or inactive plate (1).The present invention
Another to have one piece of exercise stress (6) with plane C (5) (working surface), the physical absorption of the plane C (5) of exercise stress (6) is special
Property is identical everywhere, and plane C (5) is the coating surface on the natural surface or exercise stress (6) of exercise stress (6).Make movement
Tablet (6) is matched with inactive plate (1), and the plane C (5) and the plane A (2) of inactive plate (1) for making exercise stress (6) are mutually flat
Row, full of lubricating oil (7) in the gap between inactive plate (1) and exercise stress (6), the plane C (5) of exercise stress (6) and
The distance between plane A (2) of inactive plate (1) is that bearing inlets area lubricating oil (7) film thickness is hi, definition：ψ=l2/l1,
The present invention claims：Interface shear strength τ between lubricating oil (7) and plane C (5)sbMore than the boundary between lubricating oil (7) and plane A (2)
Face shear strength τsa,AndInterface between lubricating oil (7) and plane B (3)
Shear strength τscMore than the absolute value of the shear stress at plane B (3), i.e.,：In this way, lubricating oil
(7) film just generates sliding on plane A (2) and entire plane C (5), and lubricating oil (7) film does not slide then on plane B (3)；
Here, u is movement velocity of the exercise stress (6) relative to inactive plate (1), and η is dynamic viscosity when lubricating oil (7) works,
λh=ho/hi, hoIt is bearing outlet area lubricating oil (7) film thickness, l1It is the width of the plane A (2) of inactive plate (1), l2It is quiet
The only width of the plane B (3) of plate (1).The direction of motion of exercise stress (6) is plane A (2) one end by inactive plate (1)
It is directed toward plane B (3) one end of inactive plate (1).Material is thus formed at signified entire moving surface of the invention and inlet regions
All occurs the special-shaped ladder bearing of interface sliding at static surface.The optimal operating condition of bearing of the present invention is：ψ=l2/l1=0.6；
On this condition, this bearing has 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 ladder bearing is not achieved.Bearing of the present invention has certain bearing capacity and relatively low friction coefficient, has good profit
Lubricating oil film can play preferable antifriction energy-saving effect, be used as bearing part on mechanical equipment.
In embodiment, all there is the special-shaped ladder of interface sliding at this kind of entire moving surface and at inlet region static surface
Bearing forms this bearing by inactive plate (1) and exercise stress (6), and two boards block is made, but be not excluded for of various trade mark steel
It is made using other materials.All there is the special-shaped ladder of interface sliding at this kind of entire moving surface and at inlet region static surface
Bearing, the interface shear strength τ between lubricating oil (7) and plane C (5)sbMore than the interface shearing between lubricating oil (7) and plane A (2)
Intensity τsa,AndInterface shear strength between lubricating oil (7) and plane B (3)
τscMore than the absolute value of the shear stress at plane B (3), i.e.,：In this way, lubricating oil (7) film exists
Sliding is just generated on plane A (2) and entire plane C (5), and lubricating oil (7) film does not slide then on plane B (3)；Here, hi
The distance between plane C (5) and the plane A (2) of inactive plate (1) for exercise stress (6) i.e. bearing inlets area lubricating oil (7)
Film thickness, ψ=l2/l1, l1It is the width of the plane A (2) of inactive plate (1), l2It is the width of the plane B (3) of inactive plate (1)
Degree, u are movement velocity of the exercise stress (6) relative to inactive plate (1), dynamic viscosity when η is lubricating oil (7) work, λh
=ho/hi, hoIt is bearing outlet area lubricating oil (7) film thickness.Exercise stress (6) is slided with speed u relative to inactive plate (1),
The direction of speed u is by plane B (3) one end of plane A (2) one end direction inactive plate (1) of inactive plate (1), such as Fig. 5.
Plane A (2) is to hate oil coating surface, and plane B (3) is the oleophylic natural surface of oleophylic coating surface or inactive plate (1), is put down
Face C (5) is the coating surface on the natural surface or exercise stress (6) of exercise stress (6).
Fig. 5 provides the structure diagram of embodiment bearing.In Fig. 5, u is exercise stress (6) relative to inactive plate (1)
Movement velocity, load of the w for the bearing of unit contact length upper bearing (metal), l1Width, that is, axis of plane A (2) for inactive plate (1)
Hold the width of inlet region, l2The width in width, that is, bearing outlet area of the plane B (3) for inactive plate (1), Δ h are cascaded surface
(4) step size of height, that is, bearing, hiFor bearing inlets area lubricating oil (7) film thickness, hoFor bearing outlet area lubricating oil
(7) film thickness；Lubricating oil (7) film generates sliding on plane A (2) and entire plane C (5), and lubricating oil (7) film is in plane B
(3) it is not slid on；Full of lubricating oil (7) in gap between two plates, plane A (2) is to hate oil coating surface, and plane B (3) is
The oleophylic natural surface of oleophylic coating surface or inactive plate (1), plane C (5) be exercise stress (6) natural surface or
Coating surface on exercise stress (6).
Compared with conventional fluid hydrodynamic lubrication ladder bearing shown in Fig. 4, bearing of the present invention has substantial variations in structure,
It is breached the forbidden zone of conventional lubrication technology, is realized lubricating oil film lubrication, have one using the gap dissipated between bearing surface
Fixed bearing capacity and relatively low friction coefficient.Bearing mnanufacture of the present invention is easy, of low cost, has good lubrication, antifriction, section
Energy performance, suitable for specific occasion.Therefore, the technical advantage of bearing of the present invention and application value are fairly obvious.
In embodiment, exercise stress (6) and inactive plate (1) are steel manufacture, and the plane A (2) of inactive plate (1) is
(hating oil) fluororine-carbon coating surface, the plane B (3) of inactive plate (1) are (oleophylic) coating of titanium dioxide surface, exercise stress
(6) plane C (5) is the natural surface of exercise stress (6), and lubricating oil (7) is 5P4E polyphenyl ether oils, lubricating oil (7) during work
Interface shear strength τ between plane A (2)saFor 0.02MPa, the interface shear strength τ between lubricating oil (7) and plane C (5)sb
For 0.05MPa, the interface shear strength τ between lubricating oil (7) and plane B (3)scFor 0.4MPa, power glues when lubricating oil (7) works
It spends for η=0.04Pas, the movement velocity of exercise stress (6) is u=10m/s, bearing inlets area lubricating oil (7) film thickness hi
It is 2 μm.During bearing working, lubricating oil (7) film slides on plane A (2) and entire plane C (5), and lubricating oil (7) film is flat
Face B does not slide on (3).
(1) work as l1=5mm, l2=3mm, when the height of cascaded surface (4) is h=0.4 μm of Δ, obtained bearing list of the present invention
Bit length dimension bearing capacity is w=7.17 × 105N/m, the friction coefficient on inactive plate (1) are 0.00085, exercise stress
(6) friction coefficient on is 0.001.
(2) work as l1=5mm, l2=3mm, when the height of cascaded surface (4) is h=0.8 μm of Δ, obtained bearing list of the present invention
Bit length dimension bearing capacity is w=5.44 × 105N/m, the friction coefficient on inactive plate (1) are 0.0011, exercise stress (6)
On friction coefficient be 0.001.
(3) work as l1=5mm, l2=3mm, when the height of cascaded surface (4) is h=1.2 μm of Δ, obtained bearing list of the present invention
Bit length dimension bearing capacity is w=4.16 × 105N/m, the friction coefficient on inactive plate (1) are 0.00137, exercise stress
(6) friction coefficient on is 0.00112.
(4) work as l1=5mm, l2=3mm, when the height of cascaded surface (4) is h=1.6 μm of Δ, obtained bearing list of the present invention
Bit length dimension bearing capacity is w=2.88 × 105N/m, the friction coefficient on inactive plate (1) are 0.00165, exercise stress
(6) friction coefficient on is 0.0013.
Find out from embodiment, bearing of the present invention belongs to a kind of special-shaped ladder bearing, and the bearing surface gap of its inlet region is low
In the bearing surface gap of its outlet area.Bearing of the present invention have certain bearing capacity, have good lubricating oil film and compared with
Low friction coefficient, anti-friction wear-resistant is good, is competent at specific workplace, for the bearing of main shaft in mechanical equipment, solves
The indeterminable technical problem of plain bearing.
The principle of the invention is described as follows：
It is theoretical according to the interface sliding established before, in bearing of the present invention, since lubricating oil (7) film is in inactive plate
(1) it slides and is not slid on plane B (3) on plane A (2) and the entire plane C (5) of exercise stress (6), such as Fig. 5, even if
In the case of in bearing inlets area, surface gap is less than bearing outlet area surface gap, in the case where the movement of exercise stress (6) drives,
Lubricating oil (7) flow for flowing into bearing is more than lubricating oil (7) flow of outflow bearing.In this way, the stream of the fluid flowing in bearing
Amount equilibrium condition is just broken, and constantly accumulation is squeezed to form oil pressure lubricating oil (7) within the bearing.It is formed in bearing
Lubricating oil (7) film pressure makes to generate pressure gradient flow (i.e. Poiseuille flowings) in bearing inlets area and outlet area respectively,
The pressure gradient flow generated in inlet region and outlet area respectively reduces lubricating oil (7) flow of inflow bearing, makes outflow axis
Lubricating oil (7) flow increase held, finally makes lubricating oil (7) total flow of inflow bearing be equal to the lubricating oil (7) of outflow bearing
Total flow, so as to maintain the flowing continuity of lubricating oil (7) within the bearing.This is to say, since lubricating oil (7) film is static
It slides and is not slid on plane B (3) on the plane A (2) of plate (1) and the entire plane C (5) of exercise stress (6), suitable
Bearing step size Δ h under, lubricating oil (7) film pressure, lubricating oil (7) membrane pressure of formation can be necessarily formed in bearing of the present invention
Power makes the ability that bearing of the present invention has bearing load.Presence and lubricating oil (7) due to lubricating oil (7) film and plane A (2) and
Interface shear strength between plane C (5) is relatively low, and bearing of the present invention has relatively low friction coefficient, and bearing surface abrasion is extremely light
It is micro-.Here it is the principles of bearing of the present invention.
Fig. 6 is lubricating oil (7) film pressure distribution schematic diagram in bearing of the present invention in embodiment, and ordinate is lubricating oil
(7) film pressure.
Fig. 7 is provided when α=2.5 × 10-4, U=10 and ψ=0.6 when the embodiment of the present invention in different Δ H lower bearings in
Dimensionless lubricating oil (7) film pressure is distributed.In Fig. 7, α=hi/(l1+l2), ψ=l2/l1, U=u η/(τsahi), Δ H=Δs h/
hi, X=x/ (l1+l2), P=phi/[τsa(l1+l2)], p is lubricating oil (7) film pressure.As can be seen from Figure 7, as Δ H reduces, this
Lubricating oil (7) film pressure in invention bearing constantly increases.
Fig. 8 is provided when α=2.5 × 10-4The dimensionless of bearing under Δ H different with during U=10 in the embodiment of the present invention is held
Carrying capacity W with ψ change curve.In Fig. 8, W=whi/[τsa(l1+l2)2], w is the load of contact unit length upper bearing (metal) bearing,
The definition of α, ψ, U and Δ H are identical in Fig. 7 respectively.As can be seen from Figure 8, for given U and Δ H, as ψ=l2/l1=0.6
When, the bearing capacity of bearing of the present invention reaches maximum.
Fig. 9 is provided when α=2.5 × 10-4With the bearing in the embodiment of the present invention under different U values during ψ=0.6 and Δ H values
Friction coefficient f at inactive plate (1)aValue.In Fig. 9, the definition of α, ψ, U and Δ H are identical in Fig. 7 respectively.In terms of Fig. 9
Go out, the friction co-efficient value at the inactive plate (1) of bearing of the present invention is than relatively low, this friction co-efficient value even compares conventional flow
The friction co-efficient value of body lubrication ladder bearing is much lower.This shows that bearing of the present invention has preferable antifriction and energy-saving effect.From Fig. 9
It is also seen that as Δ H increases, the friction co-efficient value (f at the inactive plate (1) of bearing of the present inventiona) increase, and with the increasing of U
Greatly, the friction co-efficient value (f at the inactive plate (1) of bearing of the present inventiona) reduce.
Figure 10 is provided when α=2.5 × 10-4With the bearing in the embodiment of the present invention under different U values during ψ=0.6 and Δ H values
Friction coefficient f at exercise stress (6)bValue.In Figure 10, the definition of α, ψ, U and Δ H are identical in Fig. 7 respectively.In terms of Figure 10
Go out, the friction co-efficient value at the exercise stress (6) of bearing of the present invention is than relatively low, this friction co-efficient value even compares conventional flow
The friction co-efficient value of body lubrication ladder bearing is much lower.This shows that bearing of the present invention has preferable antifriction and energy-saving effect.From figure
10 are also seen that as Δ H increases, the friction co-efficient value (f at the exercise stress (6) of bearing of the present inventionb) increase, and with U's
Increase, the friction co-efficient value (f at the exercise stress (6) of bearing of the present inventionb) reduce.
Claims (3)
1. all occurs the special-shaped ladder bearing of interface sliding at a kind of entire moving surface and at inlet region static surface, including one
Block inactive plate (1), the working surface of inactive plate (1) include plane A (2), plane B (3) and cascaded surface (4), plane A (2)
It is mutually parallel with plane B (3), cascaded surface (4) is vertical with plane A (2) and plane B (3) respectively, height, that is, rank of cascaded surface (4)
Step-wedge cun is Δ h；It is another to have one piece of exercise stress (6) with plane C (5), exercise stress (6) is made to be matched with inactive plate (1),
The plane C (5) of exercise stress (6) is made to be mutually parallel with the plane A (2) of inactive plate (1), the direction of motion of exercise stress (6)
To be directed toward plane B (3) one end of inactive plate (1), inactive plate (1) and movement by plane A (2) one end of inactive plate (1)
Full of lubricating oil (7), the plane C (5) of exercise stress (6) and the plane A (2) of inactive plate (1) in gap between tablet (6)
The distance between i.e. bearing inlets area lubricating oil (7) film thickness be hi, definition：ψ=l2/l1, it is characterised in that：Plane A's (2)
Physical adsorption characteristic and the physical adsorption characteristic of plane B (3) differ, and plane A (2) is to hate oil coating surface, and plane B (3) is
The oleophylic natural surface of oleophylic coating surface or inactive plate (1), plane C (5) be exercise stress (6) natural surface or
Coating surface on exercise stress (6), lubricating oil (7) film generate sliding, lubricating oil on plane A (2) and entire plane C (5)
(7) film does not generate sliding on plane B (3)；Interface shear strength τ between lubricating oil (7) and plane C (5)sbMore than lubricating oil
(7) the interface shear strength τ between plane A (2)sa,AndLubricating oil (7)
Interface shear strength τ between plane B (3)scMore than the absolute value of the shear stress at plane B (3)；In this way, lubricating oil (7) film exists
Sliding is just generated on plane A (2) and entire plane C (5), and lubricating oil (7) film does not slide then on plane B (3)；Here, u is
Exercise stress (6) is relative to the movement velocity of inactive plate (1), dynamic viscosity when η is lubricating oil (7) work, λh=ho/hi,
hoIt is bearing outlet area lubricating oil (7) film thickness, l1It is the width of the plane A (2) of inactive plate (1), l2It is inactive plate (1)
Plane B (3) width.
2. all there is the special-shaped rank of interface sliding at entire moving surface as described in claim 1 and at inlet region static surface
Terraced bearing, it is characterised in that：This optimal operating condition of bearing is：ψ=l2/l1=0.6, on this condition, this bearing has
Maximum load-carrying capacity.
3. all there is the special-shaped rank of interface sliding at entire moving surface as described in claim 1 and at inlet region static surface
Terraced bearing, it is characterised in that：The plane A (2) of inactive plate (1) is fluororine-carbon coating surface, and the plane B (3) of inactive plate (1) is
Coating of titanium dioxide surface, the plane C (5) of exercise stress (6) is steel components natural surface.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711500208.XA CN108204406A (en) | 2017-12-29 | 2017-12-29 | All there is the special-shaped ladder bearing of interface sliding at entire moving surface and at inlet region static surface |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711500208.XA CN108204406A (en) | 2017-12-29 | 2017-12-29 | All there is the special-shaped ladder bearing of interface sliding at entire moving surface and at inlet region static surface |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108204406A true CN108204406A (en) | 2018-06-26 |
Family
ID=62605278
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711500208.XA Withdrawn CN108204406A (en) | 2017-12-29 | 2017-12-29 | All there is the special-shaped ladder bearing of interface sliding at entire moving surface and at inlet region static surface |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108204406A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
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|---|---|---|---|---|
| US5492415A (en) * | 1993-08-16 | 1996-02-20 | Lemforder Metallwaren Ag | Plain bearing for chassis parts in motor vehicles |
| JPH10252757A (en) * | 1997-03-14 | 1998-09-22 | Asmo Co Ltd | Sintered oil-impregnated bearing and manufacture thereof |
| CN101398030A (en) * | 2008-11-14 | 2009-04-01 | 淮海工学院 | Anti friction high bearing capacity micro precision bearing |
| CN101765718A (en) * | 2007-07-31 | 2010-06-30 | Ntn株式会社 | Fluid dynamic bearing device and its assembling method |
| CN102954110A (en) * | 2011-08-30 | 2013-03-06 | 优磁科技股份有限公司 | Bearing assembly with high lubrication efficiency |
| CN107061501A (en) * | 2017-06-06 | 2017-08-18 | 袁虹娣 | The miniature ladder bearing of abnormity |
-
2017
- 2017-12-29 CN CN201711500208.XA patent/CN108204406A/en not_active Withdrawn
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5492415A (en) * | 1993-08-16 | 1996-02-20 | Lemforder Metallwaren Ag | Plain bearing for chassis parts in motor vehicles |
| JPH10252757A (en) * | 1997-03-14 | 1998-09-22 | Asmo Co Ltd | Sintered oil-impregnated bearing and manufacture thereof |
| CN101765718A (en) * | 2007-07-31 | 2010-06-30 | Ntn株式会社 | Fluid dynamic bearing device and its assembling method |
| CN101398030A (en) * | 2008-11-14 | 2009-04-01 | 淮海工学院 | Anti friction high bearing capacity micro precision bearing |
| CN102954110A (en) * | 2011-08-30 | 2013-03-06 | 优磁科技股份有限公司 | Bearing assembly with high lubrication efficiency |
| CN107061501A (en) * | 2017-06-06 | 2017-08-18 | 袁虹娣 | The miniature ladder bearing of abnormity |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
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