CN108591246B

CN108591246B - Special-shaped stepped bearing applying interface sliding

Info

Publication number: CN108591246B
Application number: CN201711398787.1A
Authority: CN
Inventors: 张永斌; 王俊彦; 袁虹娣
Original assignee: Chongqing Steady Technology Co ltd
Current assignee: Chongqing Steady Technology Co.,Ltd.
Priority date: 2017-12-09
Filing date: 2017-12-09
Publication date: 2021-05-04
Anticipated expiration: 2037-12-09
Also published as: CN108591246A

Abstract

The invention relates to a special-shaped stepped bearing applying interface sliding, which comprises a static plate and a moving plate, wherein the working surface of the static plate is a stepped surface, the convex working surfaces of the moving plate and the static plate are parallel to each other, the gap between the two plates in a bearing inlet area is smaller than the gap between the two plates in a bearing outlet area, lubricating oil is filled in the gap between the two plates, and the moving direction of the moving plate is from the bearing inlet area to the bearing outlet area. The working surface of the stationary plate in the bearing inlet region is an oleophobic coated surface, and the remaining working surfaces of the bearing are oleophilic surfaces. The lubricating oil film slides on the working surface of the static plate in the bearing inlet area, and the lubricating oil film does not slide on the rest surfaces of the bearing. The bearing has certain bearing capacity and lower friction coefficient, has obvious antifriction and energy-saving effects, and is used as a bearing part in mechanical equipment in specific occasions.

Description

Special-shaped stepped bearing applying interface sliding

Technical Field

The invention relates to the field of bearings, in particular to a special-shaped stepped bearing applying interface slippage.

Background

Bearings are important mechanical parts for supporting shaft parts. The sliding bearing and the rolling bearing are mainly divided into two types. The following main performance requirements are imposed on the bearing: bearing accuracy, bearing stiffness, low coefficient of friction and wear resistance. This requires that the bearing be a very delicate mechanical component and that it have a sufficient load-bearing capacity. In order to achieve good antifriction and wear resistance, the bearings also need to have good lubrication properties. The development of the bearing technology to date is mature, but the bearing technology is established on the basis of the traditional lubrication theory. At present, rolling bearings and sliding bearings are applied to different occasions and have advantages respectively. Since the present invention relates to sliding bearings, the types and techniques of existing sliding bearings are summarized as follows:

from the lubrication mechanism, the sliding bearing is classified into a hybrid friction sliding bearing and a fluid lubrication sliding bearing. The former relies on the boundary adsorption film and the hydrodynamic pressure effect to realize lubrication, and is used for low-speed, light-load and unimportant occasions; the latter relies on fluid films to achieve lubrication, which is used in important situations and more widely. The fluid lubrication sliding bearing is a main body of the sliding bearing and is divided into a fluid dynamic pressure lubrication sliding bearing and a fluid static pressure lubrication sliding bearing. The hydrostatic lubrication sliding bearing is supplied with oil by an external hydraulic system, supports load by oil pressure, is lubricated by hydraulic oil, has high manufacturing precision, complex structure and high cost, and is used for important occasions requiring high supporting rigidity, high supporting precision and high bearing capacity. The hydrodynamic lubrication sliding bearing realizes lubrication by means of hydrodynamic effect, has the advantages of simple structure, low cost and good performance, and is a common sliding bearing with wider application. It is divided into hydrodynamic lubrication centripetal sliding bearing and hydrodynamic lubrication thrust sliding bearing. The former is used to support radial loads and the latter is used to support axial loads. The type of the existing predominantly hydrodynamic lubrication thrust sliding bearing and its features are described below.

An inclined plane pad bearing, such as that shown in figure 1. It relies on the convergence gap formed between the upper and lower surfaces and the relative motion between these two surfaces to achieve the hydrodynamic effect, thereby achieving lubrication. The bearing has great bearing capacity and good antifriction and wear resistance.

Such bearings are classified into a fixed pad bearing in which both the upper and lower surfaces are not rotatable about a fulcrum, and a tilting pad bearing in which one surface is rotatable about a fulcrum. With good design, tilting pad bearings have a greater load carrying capacity than fixed pad bearings.

A sawtooth pad bearing, as shown in figure 2. The working and lubricating mechanism of the bearing is the same as that of the bearing. Its load capacity is much lower than the previous bearing under the same conditions.

And thirdly, a bevel platform pad bearing, which is shown in figure 3. The working and lubricating mechanisms of the bearing are the same as those of the bearing. Under the same working condition, the maximum bearing capacity of the bearing is 20% higher than that of the bearing with the inclined plane fixed pad.

And fourthly, a Rayleigh step bearing, wherein the bearing is shown in figure 4. The working and lubricating mechanism of the bearing is the same as that of the previous bearing. Compared with the three bearings, the bearing has the highest maximum bearing capacity under the same working condition, and is 28% higher than the maximum bearing capacity of the inclined plane fixed pad bearing.

According to the conventional fluid lubrication theory, the conventional bearings shown in fig. 1-4 all rely on a convergent wedge-shaped gap formed between two solid surfaces, and under the driving of a moving surface, lubricating oil is brought in from a large section of the convergent wedge-shaped gap and brought out from a small section of the convergent wedge-shaped gap, so that the lubricating oil is extruded in the convergent wedge-shaped gap to generate oil pressure, and a lubricating oil film has bearing capacity, thereby forming the fluid dynamic pressure lubrication bearing. According to the conventional fluid lubrication theory, it is impossible to form a hydrodynamic lubricating oil film in a divergent wedge-shaped gap formed between two solid surfaces, and then it is impossible to form a bearing. Because at this moment under the motion surface drive, lubricating oil is taken into from the little section of dispersing the wedge clearance, and is taken out from its big cross-section, lubricating oil just can not receive the extrusion in dispersing the wedge clearance like this, just can not produce the oil pressure yet, does not possess the bearing capacity, can not form the lubricating oil film.

Disclosure of Invention

The invention aims to provide a special-shaped stepped bearing applying interface sliding. Contrary to conventional fluid lubrication theory, such bearings have a diverging gap between the two contacting surfaces. In contrast to the conventional stepped bearing shown in fig. 4, the surface clearance of the inlet region of such a bearing is smaller than the surface clearance of its outlet region. According to the conventional fluid lubrication theory, this bearing should be unpractical, since the lubricant is brought in from the small cross section of the diverging gap and out from its large cross section, and the lubricant is not squeezed in such a gap, and no oil pressure is formed, and no load-carrying capacity is obtained. However, if the stationary contact surface of the bearing inlet area is an oleophobic coating surface with weaker physical adsorption capacity, so that the lubricating oil film slides on the stationary contact surface of the bearing inlet area, and the lubricating oil film does not slide on the rest surfaces of the bearing, the sliding of the lubricating oil film on the stationary contact surface of the bearing inlet area causes the flow rate of the lubricating oil flowing into the small section of the bearing inlet area to be larger than the flow rate of the lubricating oil flowing out of the large section of the bearing outlet area under the driving of the moving surface, so that the lubricating oil can be extruded in the divergent gap to generate oil pressure, and the lubricating oil film has bearing capacity. Thus, the special-shaped stepped bearing is formed.

The special-shaped stepped bearing with certain bearing capacity is realized by only applying an interface sliding technology under the condition of a divergent gap which is avoided in the traditional bearing. The bearing has the advantages of easy manufacture, simple structure and low cost.

The technical solution of the invention is as follows:

a special-shaped stepped bearing applying interface sliding comprises a static plate (1), as shown in figure 5, wherein the working surface of the static plate (1) comprises a plane A (2), a plane B (3) and a stepped surface (4), the plane A (2) and the plane B (3) are parallel to each other, the stepped surface (4) is respectively perpendicular to the plane A (2) and the plane B (3), and the height of the stepped surface (4), namely the stepped size is delta h; the physical adsorption characteristics of plane a (2) are different from those of plane B (3), plane a (2) being an oleophobic coated surface and plane B (3) being an oleophilic coated surface or an oleophilic natural surface of a stationary plate (1). The invention also has a motion plate (6) with a plane C (5), the plane C (5) being either the oleophilic natural surface of the motion plate (6) or the oleophilic coated surface on the motion plate (6). The moving flat plate (6) is matched with the static plate (1), the plane C (5) of the moving flat plate (6) is parallel to the plane A (2) of the static plate (1), a gap between the static plate (1) and the moving flat plate (6) is filled with lubricating oil (7), and the distance between the plane C (5) of the moving flat plate (6) and the plane A (2) of the static plate (1), namely the thickness of the lubricating oil (7) film in the bearing inlet area is h_iThe invention requires:

thus, the lubricating oil (7) film slips on the plane A (2), where τ_saIs the interfacial shear strength between the lubricant (7) and the plane A (2), u is the speed of movement of the moving plate (6) relative to the stationary plate (1), η is the kinematic viscosity of the lubricant (7) during operation, λ_h＝h_o/h_i，h_oIs the thickness of the lubricating oil (7) film in the bearing outlet region. The moving direction of the moving flat plate (6) is from one end of the plane A (2) of the static plate (1) to one end of the plane B (3) of the static plate (1). The lubricating oil (7) film slips on the plane A (2), and the lubricating oil (7) film does not slip on the plane B (3) or the plane C (5), so that the special-shaped step bearing is formed. The optimal working conditions of the bearing are as follows:

here, λ_h＝h_o/h_i，l₁The width of the plane A (2) of the stationary plate (1), i.e. the width of the bearing inlet zone,/₂The width of a plane B (3) of the static plate (1), namely the width of the bearing outlet area; in this condition, the bearing has the maximum load capacity.

Further, the plane A (2) of the static plate (1) is a fluorocarbon coating surface, the plane B (3) of the static plate (1) is a titanium dioxide coating surface, and the plane C (5) of the moving plate (6) is a titanium dioxide coating surface.

The invention has the beneficial effects that:

the invention designs a special-shaped stepped bearing by using an interface sliding technology and a surface coating method. The bearing is suitable for occasions where the surface clearance of the bearing inlet area is smaller than that of the bearing outlet area, which cannot be achieved by the traditional step bearing. The bearing has certain bearing capacity, lower friction coefficient and good lubricating oil film, can play a good role in reducing friction and saving energy, and is used as a bearing part on mechanical equipment.

The invention has the following advantages:

(1) the bearing is suitable for occasions that the surface clearance of the bearing inlet area is smaller than that of the bearing outlet area.

(2) The bearing of the invention contains a good lubricating oil film, has good antifriction and energy-saving performance and has certain bearing capacity.

(3) The bearing has the advantages of simple structure, easy manufacture and low cost.

Drawings

FIG. 1 is a schematic structural view of a prior art inclined plane pad bearing;

FIG. 2 is a schematic structural diagram of a conventional sawtooth pad bearing;

FIG. 3 is a schematic structural view of a prior art ramp platform pad bearing;

FIG. 4 is a schematic structural diagram of a conventional Rayleigh step bearing;

FIG. 5 is a schematic structural diagram of a special-shaped step bearing using interface sliding according to an embodiment of the present invention;

FIG. 6 is a schematic view showing the pressure distribution of the lubricating oil (7) film in the bearing of the present invention in the embodiment;

FIG. 7 is a film pressure profile of a dimensionless lubricant (7) in a bearing of the present invention at different Δ H in the examples;

FIG. 8 is a graph of the dimensionless bearing capacity W of the bearing of the present invention at different values of U and Δ H in the examples;

FIG. 9 is a graph of dimensionless bearing load W versus ψ for bearings of the present invention at different Δ H in the examples;

FIG. 10 shows the coefficient of friction f at the stationary plate (1) of the bearing in an embodiment of the invention at different values of U and Δ H_aA graph of values;

FIG. 11 shows the coefficient of friction f at the moving plate (6) of the bearing in the embodiment of the invention for different values of U and Δ H_bA map of values.

Where u is the speed of movement of the moving plate relative to the stationary plate, w is the load supported by the bearing per unit contact length, l₁The width of the plane A (2) of the stationary plate (1), i.e. the width of the bearing inlet zone,/₂The width of a plane B (3) of the static plate (1), namely the width of an outlet area of the bearing, delta h is the height of a step surface (4), namely the step size of the bearing, h_iThickness of lubricating oil (7) film in bearing entrance region, h_oThe thickness of the lubricating oil (7) film in the outlet area of the bearing; lubricating oil is filled in a gap between the two plates, the lubricating oil (7) film slides on the plane A (2), and the lubricating oil (7) film does not slide on the plane B (3) and the plane C (5).

In fig. 5: 1-static plate, 2-plane A, 3-plane B, 4-step surface, 5-plane C, 6-moving flat plate and 7-lubricating oil

Detailed Description

Preferred embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

Examples

The utility model provides an application interface gliding dysmorphism step bearing, as figure 5, including a static plate (1), the working surface of static plate (1) includes plane A (2), plane B (3) and ladder face (4), and plane A (2) and plane B (3) are parallel to each other, and ladder face (4) are perpendicular with plane A (2) and plane B (3) respectively, and the height of ladder face (4) is the rank promptlyThe ladder size is delta h; the physical adsorption characteristics of plane a (2) are different from those of plane B (3), plane a (2) being an oleophobic coated surface and plane B (3) being an oleophilic coated surface or an oleophilic natural surface of a stationary plate (1). The invention also has a motion plate (6) with a plane C (5), the plane C (5) being either the oleophilic natural surface of the motion plate (6) or the oleophilic coated surface on the motion plate (6). The moving flat plate (6) is matched with the static plate (1), the plane C (5) of the moving flat plate (6) is parallel to the plane A (2) of the static plate (1), a gap between the static plate (1) and the moving flat plate (6) is filled with lubricating oil (7), and the distance between the plane C (5) of the moving flat plate (6) and the plane A (2) of the static plate (1), namely the thickness of the lubricating oil (7) film in the bearing inlet area is h_iThe invention requires:

The bearing is suitable for occasions where the surface clearance of the bearing inlet area is smaller than that of the bearing outlet area, which cannot be achieved by the traditional step bearing. The bearing has certain bearing capacity, lower friction coefficient and good lubricating oil film, can play a good role in reducing friction and saving energy, and is used as a bearing part on mechanical equipment.

In the embodiment, the special-shaped stepped bearing using interface sliding comprises a static plate (1) and a moving flat plate (6), wherein the two plates are made of various grades of steel, but the use of other materials is not excluded. According to the special-shaped stepped bearing applying interface sliding, the distance between the plane C (5) of the moving flat plate (6) and the plane A (2) of the static plate (1), namely the thickness h of the lubricating oil (7) film in the inlet area of the bearing_iIt must satisfy:

thus, the lubricating oil (7) film slips on the plane A (2), where τ_saIs the interfacial shear strength between the lubricant (7) and the plane A (2), u is the speed of movement of the moving plate (6) relative to the stationary plate (1), η is the kinematic viscosity of the lubricant (7) during operation, λ_h＝h_o/h_i，h_oIs the thickness of the lubricating oil (7) film in the bearing outlet region. The moving plate (6) slides with respect to the stationary plate (1) at a speed u, in the direction from the end of the plane a (2) of the stationary plate (1) to the end of the plane B (3) of the stationary plate (1), as shown in fig. 5. The lubricating oil (7) film produces slippage on plane a (2), the lubricating oil (7) film does not produce slippage on plane B (3) and plane C (5), plane a (2) is an oleophobic coated surface, plane B (3) is an oleophilic coated surface or an oleophilic natural surface of a stationary plate (1), and plane C (5) is an oleophilic natural surface of a moving plate (6) or an oleophilic coated surface on a moving plate (6).

FIG. 5 is a schematic structural view of a bearing according to an embodiment. In fig. 5, u is the speed of movement of the moving plate (6) relative to the stationary plate (1), w is the load of the bearing support per unit contact length, l₁The width of the plane A (2) of the stationary plate (1), i.e. the width of the bearing inlet zone,/₂The width of a plane B (3) of the static plate (1), namely the width of an outlet area of the bearing, delta h is the height of a step surface (4), namely the step size of the bearing, h_iIs the bearing inlet areaThickness of lubricating oil (7) film, h_oThe thickness of the lubricating oil (7) film in the outlet area of the bearing; the lubricating oil (7) film generates slippage on the plane A (2), and the lubricating oil (7) film does not generate slippage on the plane B (3) and the plane C (5); the gap between the two plates is filled with lubricating oil (7), plane A (2) is an oleophilic coating surface, plane B (3) is an oleophilic coating surface or an oleophilic natural surface of the stationary plate (1), and plane C (5) is an oleophilic natural surface of the moving plate (6) or an oleophilic coating surface on the moving plate (6).

Compared with the traditional fluid dynamic pressure lubrication stepped bearing shown in fig. 4, the bearing of the invention has substantial change in structure, adopts the divergent gaps between the bearing surfaces, breaks through the forbidden zone of the traditional lubrication technology, realizes lubrication of a lubricating oil film, and has certain bearing capacity and lower friction coefficient. The bearing of the invention has the advantages of easy manufacture, low cost, good lubricating, antifriction and energy-saving performances and suitability for specific occasions. Therefore, the technical advantages and application values of the bearing are quite obvious.

In the examples, the moving plate (6) and the stationary plate (1) are made of steel, the plane a (2) of the stationary plate (1) is an (oleophobic) fluorocarbon coating surface, the plane B (3) of the stationary plate (1) is an (oleophilic) titanium dioxide coating surface, the plane C (5) of the moving plate (6) is an (oleophilic) titanium dioxide coating surface, the lubricating oil (7) is domestic No. 30 engine oil, and the interfacial shear strength τ between the lubricating oil (7) and the plane a (2) is achieved during operation_sa0.01MPa, the dynamic viscosity eta of lubricating oil (7) when working is 0.01 Pa.s, the moving speed u of moving flat plate (6) is 10m/s, and the thickness h of lubricating oil (7) film in the bearing inlet area_iIs 2 μm; when the bearing works, the lubricating oil (7) film slides on the plane A (2), and the lubricating oil (7) film does not slide on the plane B (3) and the plane C (5):

(1) when l is₁＝5mm，l₂When the height of the stepped surface (4) is 0.2 mu m at 3mm, the bearing capacity per unit length dimension of the bearing of the present invention is 1.53X 10⁶N/m, the coefficient of friction on the stationary plate (1) is 0.0008 and the coefficient of friction on the moving plate (6) is 0.0005.

(2) When l is₁＝5mm，l₂3mm, step surface (4)When the height Δ h is 0.4 μm, the bearing capacity per unit length dimension of the bearing of the present invention is 1.15 × 10⁶N/m, the friction coefficient on the static plate (1) is 0.001, and the friction coefficient on the moving plate (6) is 0.0006.

(3) When l is₁＝5mm，l₂When the height of the stepped surface (4) is 0.6 mu m and 3mm, the bearing capacity per unit length dimension of the bearing of the invention is 8.94 multiplied by 10⁵N/m, the friction coefficient on the static plate (1) is 0.0011, and the friction coefficient on the moving plate (6) is 0.0007.

(4) When l is₁＝5mm，l₂When the height of the stepped surface (4) is 0.8 mu m at 3mm, the bearing capacity per unit length dimension of the bearing of the present invention is 6.39 x 10⁵N/m, the friction coefficient on the static plate (1) is 0.0014, and the friction coefficient on the moving plate (6) is 0.0009.

(5) When l is₁＝5mm，l₂When the height of the stepped surface (4) is equal to 3mm and the height deltah is equal to 1.0 mu m, the bearing capacity per unit length dimension of the bearing is 4.48 multiplied by 10⁵N/m, the friction coefficient on the static plate (1) is 0.002, and the friction coefficient on the moving flat plate (6) is 0.0013.

(6) When l is₁＝5mm，l₂When the height of the stepped surface (4) is equal to 3mm and the height is equal to 1.2 mu m, the bearing capacity per unit length dimension of the bearing is 2.56 multiplied by 10⁵N/m, the friction coefficient on the static plate (1) is 0.0026, and the friction coefficient on the moving plate (6) is 0.0026.

(7) When l is₁＝5mm，l₂When the height of the stepped surface (4) is equal to 3mm and the height is equal to 1.4 mu m, the bearing capacity per unit length dimension of the bearing is 6.4 multiplied by 10⁴N/m, the friction coefficient on the static plate (1) is 0.0035, and the friction coefficient on the moving plate (6) is 0.0035.

According to the embodiment, the bearing belongs to a special-shaped step bearing, the bearing surface clearance of the inlet area of the special-shaped step bearing is lower than that of the outlet area of the special-shaped step bearing; the bearing has certain bearing capacity, lower friction coefficient and good antifriction and energy-saving performance, is applied to mechanical equipment, is competent for specific working occasions, and solves the technical problem which cannot be solved by the traditional bearing.

The principle of the invention is illustrated as follows:

according to the previously established interfacial slip theory, in the bearing designed by the invention, since the lubricating oil (7) film slips on the plane A (2) of the static plate (1) but not on the plane B (3) and the plane C (5), as shown in FIG. 5, even in the case that the surface clearance of the bearing inlet area is smaller than that of the bearing outlet area, the flow rate of the lubricating oil (7) flowing into the bearing is larger than that of the lubricating oil (7) flowing out of the bearing under the motion of the moving flat plate (6). Thus, the flow balance condition of the fluid flow in the bearing is broken, and the lubricating oil (7) is continuously accumulated in the bearing and is extruded to form oil pressure. The lubricating oil (7) film pressure formed in the bearing causes pressure gradient flows (namely Poiseuille flows) to be generated in the inlet area and the outlet area of the bearing respectively, the flow rate of the lubricating oil (7) flowing into the bearing is reduced by the pressure gradient flows generated in the inlet area and the outlet area respectively, the flow rate of the lubricating oil (7) flowing out of the bearing is increased, and finally the total flow rate of the lubricating oil (7) flowing into the bearing is equal to the total flow rate of the lubricating oil (7) flowing out of the bearing, so that the flow continuity of the lubricating oil (7) in the bearing is maintained. That is, since the lubricating oil (7) film slips on the plane a (2) of the stationary plate (1) and does not slip on the plane B (3) or the plane C (5), the lubricating oil (7) film pressure is inevitably generated in the bearing of the present invention at an appropriate bearing step size Δ h, and the generated lubricating oil (7) film pressure gives the bearing of the present invention the ability to support a load. Due to the existence of the lubricating oil (7) film and the low shearing strength of the interface between the lubricating oil (7) and the plane A (2), the bearing has a low friction coefficient, and the abrasion of the surface of the bearing is very slight or even negligible. This is the principle of the bearing of the present invention.

Fig. 6 is a schematic view showing the film pressure distribution of the lubricant (7) in the bearing of the present invention in the example, and the ordinate is the film pressure of the lubricant (7).

FIG. 7 shows that when α is 2.5 × 10^-4U10 and ψ 0.6, the film pressure distribution of the dimensionless lubricant oil (7) in the bearing at different Δ H in the embodiment of the present invention. In fig. 7, α ═ h_i/(l₁+l₂)，ψ＝l₂/l₁，U＝uη/(τ_sah_i)，ΔH＝Δh/h_i，X＝x/(l₁+l₂)，P＝ph_i/[τ_sa(l₁+l₂)]And p is the lube (7) film pressure. As seen from fig. 7, as Δ H decreases, the lubricating oil (7) film pressure in the bearing of the present invention increases.

FIG. 8 shows the value when α is 2.5 × 10^-4And ψ 0.6, the dimensionless bearing capacity W of the bearing in the embodiment of the present invention at different values of U and Δ H. In fig. 8, α, ψ, U, and Δ H are respectively defined as in fig. 7, and W ═ wh_i/[τ_sa(l₁+l₂)²]. As seen from fig. 8, as Δ H decreases, the bearing load (W) of the bearing of the present invention increases; for a given U, an excessive Δ H would cause the bearing of the invention to lose its load-bearing capacity, which is a good reflection of the conditions under which the bearing of the invention is formed:

(the rewritten form of this formula is:

). It is also seen from fig. 8 that for a given Δ H, the bearing load (W) of the bearing of the invention increases as U increases, which means that: interfacial shear strength tau between lubricating oil (7) and plane A (2)_saThe smaller (the larger U) the more severe the sliding of the lubricating oil (7) film on the plane A (2), the more the bearing of the invention can form lubricating oil (7) film pressure, and the more the bearing of the invention has the larger bearing capacity. This is a good indication of the use of interfacial slippage to form the shaped step bearing referred to in the present invention.

FIG. 9 shows the value when α is 2.5 × 10^-4And the dimensionless bearing capacity W of the bearing in the embodiment of the present invention at different Δ H when U is 10 is plotted against ψ. In fig. 9, α, ψ, U, and Δ H are defined as in fig. 7, respectively, and W is defined as in fig. 8. As can be seen from fig. 9, for a given U and Δ H, there is an optimum ψ (═ l)₂/l₁) The value at which the load bearing capacity of the bearing of the invention is maximized.

Fig. 10 shows when α is 2.510^-4Coefficient of friction f at the stationary plate (1) of the bearing in the embodiment of the present invention at different values of U and Δ H when ψ is 0.6_aThe value is obtained. In fig. 10, α, ψ, U, and Δ H are defined as in fig. 7, respectively. As can be seen from fig. 10, the coefficient of friction values at the stationary plate (1) of the bearing of the present invention is comparatively low, which is even much lower than that of the conventional fluid lubricated stepped bearing. This shows that the bearing of the present invention has good antifriction and energy saving effect. It is also seen from fig. 10 that as Δ H increases, the coefficient of friction value (f) at the stationary plate (1) of the bearing of the invention_a) Increasing and with increasing U the coefficient of friction value (f) at the stationary plate (1) of the bearing of the invention_a) And decreases.

FIG. 11 shows the value when α is 2.5 × 10^-4Coefficient of friction f at moving plate (6) of bearing in the embodiment of the present invention at different values of U and Δ H when ψ is 0.6_bThe value is obtained. In fig. 11, α, ψ, U, and Δ H are respectively defined as in fig. 7. As can be seen from fig. 11, the friction coefficient value at the moving plate (6) of the bearing of the present invention is comparatively low, which is even much lower than that of the conventional fluid lubricated stepped bearing. This shows that the bearing of the present invention has good antifriction and energy saving effect. It is also seen from fig. 11 that as Δ H increases, the coefficient of friction value (f) at the moving plate (6) of the bearing of the present invention_b) Increasing, and as U increases, the coefficient of friction (f) at the moving plate (6) of the bearing of the invention_b) And decreases.

Claims

1. A special-shaped stepped bearing utilizing interface sliding comprises a static plate (1), wherein the working surface of the static plate (1) comprises a plane A (2), a plane B (3) and a stepped surface (4), the plane A (2) and the plane B (3) are parallel to each other, the stepped surface (4) is respectively vertical to the plane A (2) and the plane B (3), and the height of the stepped surface (4), namely the stepped size, is delta h; another moving plate (6) with a plane C (5) is provided, the moving plate (6) is matched with the static plate (1), the plane C (5) of the moving plate (6) is parallel to the plane A (2) of the static plate (1), the moving direction of the moving plate (6) is that one end of the plane A (2) of the static plate (1) points to one end of the plane B (3) of the static plate (1), and the static plate (1) is provided with a plurality of moving plates (6)Lubricating oil (7) are filled in the clearance between plate (1) and motion flat plate (6), its characterized in that: the physical adsorption characteristic of the plane A (2) is different from that of the plane B (3), the plane A (2) is an oleophilic coating surface, the plane B (3) is an oleophilic coating surface or an oleophilic natural surface of the static plate (1), and the plane C (5) is an oleophilic natural surface of the moving plate (6) or an oleophilic coating surface on the moving plate (6); the plane A (2) is a fluorocarbon coating surface, the plane B (3) is a titanium dioxide coating surface, the plane C (5) is a titanium dioxide coating surface, the lubricating oil (7) is domestic No. 30 engine oil, a lubricating oil (7) film slides on the plane A (2), and the lubricating oil (7) film does not slide on the plane B (3) or the plane C (5); the distance between the plane C (5) of the moving plate (6) and the plane A (2) of the stationary plate (1), i.e. the thickness of the lubricating oil (7) film in the bearing inlet area, is h_i，h_iThe following conditional expressions must be satisfied:

thus, the lubricating oil (7) film slips on the plane A (2), where τ_saIs the interfacial shear strength between the lubricant (7) and the plane A (2), u is the speed of movement of the moving plate (6) relative to the stationary plate (1), η is the kinematic viscosity of the lubricant (7) during operation, λ_h＝h_o/h_i，h_oIs the thickness of the lubricating oil (7) film in the bearing outlet region.

2. The special-shaped stepped bearing utilizing interface sliding as claimed in claim 1, wherein: the optimal working conditions of the bearing are as follows:

here, λ_h＝h_o/h_i，h_iThickness of lubricating oil (7) film in bearing entrance region, h_oThickness of lubricating oil (7) film for bearing outlet region, /)₁The width of the plane A (2) of the stationary plate (1), i.e. the width of the bearing inlet zone,/₂Is the width, i.e. the axis, of the plane B (3) of the stationary plate (1)The width of the socket area; in this condition, the bearing has the maximum load capacity.