CN109681523B - A combined sliding surface spiral groove bearing - Google Patents

Abstract

The invention discloses a combined sliding surface spiral groove bearing, which includes a bearing bush and a rotating shaft. The rotating shaft is arranged in the bearing bush, and the rotating shaft and the bearing bush are in clearance fit. In the use state, the axis center of the rotating shaft is located below the axis center side of the bearing bush, and the gap between the bearing bush and the rotating shaft forms a convergence area and a divergence area of oil along the rotation direction of the rotating shaft. The inner wall of the bearing bush is provided with multiple oil chambers at intervals along the circumferential direction, and each oil chamber is provided with an oil inlet and an oil outlet inside. There are slip coating areas inside all oil chambers. The slip coating areas in each oil chamber located in the convergence area extend along the rotation direction of the rotating shaft, forming a slip coating extension area on the inner wall of the bearing bush. The coating in the slip coating area and the slip coating extension area is a fluorocarbon coating. The invention utilizes the slip characteristics of the fluorocarbon coating to reduce frictional resistance, reduce friction power consumption within the oil film, increase oil film pressure and end leakage, quickly take away heat, suppress the temperature rise during the high-speed rotation of the bearing, and improve the performance of the bearing at high speed. Rotating capacity.

Description

A combined sliding surface spiral groove bearing

Technical field

The present invention relates to the technical field of bearings, and in particular to a combined sliding surface spiral groove bearing.

Background technique

High-speed and ultra-high-speed cutting have gradually become the mainstream development of cutting technology and machine tools. Bearings, as an important support method, have become an important factor affecting the speed and stability of machine tools. Hydrodynamic and static pressure bearings have high load-bearing capacity, high stiffness and high rotation accuracy, and have great application potential in high-speed rotating machinery. Heating is the fundamental reason that restricts the increase in the speed of dynamic and static pressure bearings. When the speed increases, the friction power consumption within the oil film increases significantly, causing the temperature rise of the oil film to increase. In severe cases, it may even lead to "shaft holding" accidents. The problem of temperature rise is one of the main problems plaguing the field of fluid lubrication.

Existing methods of reducing temperature rise often use traditional dynamic and static pressure sliding bearing design technology lubricated with low-viscosity lubricating media. Bearings designed by traditional methods often require a long period of research and testing to discover the advantages and disadvantages of their performance. In order to maximize the advantages of existing bearings and make the bearings better used in high-speed and ultra-high-speed rotating machinery, it is required to control their temperature rise. Enhancing the working performance of the bearing contact surface through surface spraying technology has become an effective means to improve the working performance of bearings. It is of great significance for optimizing the performance of sliding bearings, improving the working efficiency and stability of mechanical systems, and promoting the development of mechanical innovation.

Contents of the invention

In view of the shortcomings of the above-mentioned prior art, the purpose of the present invention is to propose a combined sliding surface spiral groove bearing to solve the problem of excessive resistance of lubricating oil between the bearing bush and the rotating shaft, resulting in a significant increase in friction power consumption in the oil film, resulting in a bearing failure of the bearing. Due to poor force, the temperature rise of the bearing during high-speed operation is difficult to control.

In order to solve the above technical problems, the technical solution adopted by the present invention is:

A combined sliding surface spiral groove bearing includes a bearing bush and a rotating shaft. The rotating shaft is arranged in the bearing bush, and the rotating shaft and the bearing bush are in clearance fit. In the use state, the axis center of the rotating shaft is located below the axis center side of the bearing bush, and the gap between the bearing bush and the rotating shaft forms a convergence area and a divergence area of oil along the rotation direction of the rotating shaft. The inner wall of the bearing bush is provided with multiple oil chambers at intervals along the circumferential direction, and each oil chamber is provided with an oil inlet and an oil outlet inside. The inner walls of all oil chambers are equipped with slip coating areas. The slip coating areas in each oil chamber located in the convergence area extend out of the inner wall of the oil chamber along the rotation direction of the rotating shaft, forming an extension of the slip coating on the inner wall of the bearing bush. district.

Preferably, the opening of the oil chamber on the inner wall of the bearing bush is in the shape of a parallelogram, and the bottom of the oil chamber has an arc-shaped structure along the circumferential direction with high ends and a low center. The oil inlet and oil outlet are arranged at the lowest point of the bottom of the oil chamber and are distributed at both ends of the oil chamber along the axis of the bearing bush.

Preferably, the side of the opening of the oil chamber close to the oil outlet is inclined toward the rotation direction of the rotating shaft relative to the side of the oil inlet.

Preferably, the slip coating area covers the bottom of the oil chamber, is offset from the line connecting the oil inlet and the oil outlet to one side of the rotation direction of the rotating shaft, and extends to the opening edge of the oil chamber.

Preferably, the slip coating extension area covers the inner surface of the bearing bush, and its outer contour is a right-angled trapezoid. The angle between the hypotenuse of the slip coating extension area and the rotation direction of the rotating shaft is 5° to 8°.

Preferably, there are at least two slip coating extension areas located in the convergence area, and the circumferential length of each slip coating extension area decreases along the rotation direction of the rotation shaft from the maximum gap to the minimum gap between the bearing bush and the rotation shaft. The first sliding coating extension area located in the convergence area and along the rotation direction of the rotating shaft extends to the opening of its adjacent oil chamber.

Preferably, the coating of the slip coating area and the slip coating extension area is a fluorocarbon coating.

Preferably, the oil inlet and the oil outlet are respectively close to both ends of the oil chamber along the axial direction of the bearing pad.

By adopting the above technical solution, the beneficial technical effects of the present invention are: the present invention utilizes the slip characteristics of the fluorocarbon coating to reduce the frictional resistance of lubricating oil flow, reduce the frictional power consumption within the oil film, and increase the oil film pressure and end leakage. It can quickly take away the heat, suppress the temperature rise during the high-speed operation of the bearing, and improve the bearing capacity of the high-speed operation of the bearing.

Description of the drawings

Figure 1 is a schematic diagram of the structural principle of a combined sliding surface spiral groove bearing of the present invention.

Figure 2 is a schematic diagram of the circumferentially expanded structure of the bearing bush in Figure 1.

Detailed ways

The present invention will be described in detail below in conjunction with the accompanying drawings:

With reference to Figures 1 and 2, a combined sliding surface spiral groove bearing includes a bearing bush 1 and a rotating shaft 2. The rotating shaft 2 is arranged in the bearing bush 1. The bearing bush 1 is fixedly installed on the bearing seat. The rotating shaft 2 and the bearing bush 1 For clearance fit, the bearing bush 1 can be a split bearing bush or an integral bearing bush. In the present invention, an integral bearing bush is preferably used. In the use state, the rotating shaft 2 rotates at high speed inside the bearing bush 1, and the gap between the rotating shaft 2 and the bearing bush 1 is filled with lubricating oil, and the lubricating oil forms an oil film in a moving state. The axis center of the high-speed rotating shaft 2 is located on one side of the axis center of the bearing bush 1. The gap between the bearing bush 1 and the rotating shaft 2 forms the convergence area 3 and the divergence area 4 of the oil film along the rotation direction of the rotating shaft 2. The minimum gap between the rotating shaft 2 and the bearing bush 1 is At 9 and the maximum gap, the gap between the rotating shaft 2 and the bearing bush 1 is divided into two parts, one part is the above-mentioned convergence zone 3, and the other part is the above-mentioned divergence zone 4. Specifically, when the rotating shaft 2 rotates counterclockwise, the axis center of the rotating shaft 2 is located below the right side of the axis center of the bearing bush 1. When the rotating shaft 2 rotates clockwise, the axis center of the rotating shaft 2 is located below the left side of the axis center of the bearing bush 1. The embodiment of the invention takes the counterclockwise rotation direction of the rotating shaft 2 as an example to illustrate the structure and operating status of the invention. The convergence area 3 of the oil film is located at the lower part of the gap between the rotating shaft 2 and the bearing bush 1, and the divergent area 4 is located at the upper part of the gap between the rotating shaft 2 and the bearing bush 1. .

The inner wall of the bearing bush 1 is provided with three oil chambers, namely the first oil chamber 11, the second oil chamber 12, and the third oil chamber 13. The three oil chambers are spaced apart in sequence along the circumferential direction of the bearing bush 1, among which the first oil chamber 11 Located in the divergence area 4 of the oil film, the second oil chamber 12 and the third oil chamber 13 are both located in the convergence area 3 of the oil film. The openings of each oil chamber located on the inner wall of the bearing bush 1 are parallelograms, and the bottoms of the first oil chamber 11, the second oil chamber 12, and the third oil chamber 13 form an arc-shaped structure along the circumferential direction with high ends and a low center. The first oil chamber 11, the second oil chamber 12, and the third oil chamber 13 are each provided with an oil inlet 7 and an oil outlet 8. The oil inlet 7 and the oil outlet 8 are located at the lowest point of the bottom of the oil chamber. , and are distributed at both ends of the oil chamber along the axis of bearing bush 1. The side of the opening of the oil chamber close to the oil outlet 8 is inclined toward the rotation direction of the rotating shaft 2 relative to the side of the oil inlet 7 .

Taking one of the oil chambers as an example, the movement of the oil film under working conditions is explained: the lubricating oil enters the oil chamber through the oil inlet 7, moves in the oil chamber along the rotation direction of the rotating shaft 2, and moves toward the oil outlet near the oil outlet 8. One side diverges, enters the gap between the rotating shaft 2 and the bearing bush 1, and then moves along the rotation direction of the rotating shaft 2. When the oil film in the gap between the rotating shaft 2 and the bearing bush 1 moves along the rotation direction of the rotating shaft 2 to the above-mentioned oil chamber, part of the oil film close to the surface of the bearing bush 1 enters the oil chamber, moves in the oil chamber along the rotation direction of the rotating shaft 2, and moves toward the outlet. One side of the oil port 8 converges, and the bearing bush 1 is discharged from the oil outlet 8. The lubricating oil discharged through the oil outlet 8 will take away a large amount of heat and achieve the purpose of cooling.

The bottoms of the three oil chambers are each provided with a slip coating area 5. The slip coating area 5 covers each oil chamber and is located on the side of the line connecting the oil inlet 7 and the oil outlet 8 toward the rotation direction of the rotating shaft 2, and Extends to the opening edge of the oil chamber. The slip coating areas in the second oil chamber 12 and the third oil chamber 13 located in the convergence area extend their corresponding oil chambers along the rotation direction of the rotating shaft 2, forming a slip coating extension area on the inner wall of the bearing bush 1 6. The coatings in the slip coating area 5 and the slip coating extension area 6 are fluorocarbon coatings. The slip coating extension area 6 covers the inner surface of the bearing bush 1, and its outer contour is a right-angled trapezoid. The angle between the hypotenuse of the slip coating extension area 6 and the rotation direction of the rotating shaft 2 is 7°. Under working conditions, the lubricating oil enters each oil chamber through the oil inlet 7. The lubricating oil close to the slip coating area 5 quickly slides from the oil chamber along the rotation direction of the rotating shaft 2 into the gap between the rotating shaft 2 and the bearing bush 1. The transfer coating area 5 effectively reduces the resistance of the inner wall of the oil chamber to the movement of lubricating oil, and utilizes the poor adhesion of lubricating oil on the surface of the fluorocarbon coating to increase the flow rate of lubricating oil in the oil chamber.

The second oil chamber 12 and the third oil chamber 13 each have one corresponding slip coating extension area 6. The circumferential length of each slip coating extension area 6 ranges from the maximum gap between the bearing bush 1 and the rotating shaft 2 to the minimum. The gap 9 gradually decreases along the rotation direction of the rotating shaft 2 , that is, the circumferential length of the slip coating extension area 6 corresponding to the second oil chamber 12 is greater than the circumferential length of the slip coating extension area 6 corresponding to the third oil chamber 13 Length, the first slip coating extension area 6 located in the convergence area and along the rotation direction of the rotating shaft 2 (that is, the slip coating extension area 6 corresponding to the second oil chamber 12) extends to the third oil chamber 13 of the opening. The lubricating oil enters the gap between the rotating shaft 2 and the bearing bush 1 from the oil chamber and then moves with the rotating shaft. The flow rate of the lubricating oil in the convergence zone 3 is significantly lower than the flow rate of the lubricating oil in the divergent zone. The slip coating extension zone in the convergence zone 3 6 can effectively reduce the resistance of the bearing surface to the lubricating oil, increase the flow rate of the lubricating oil in the convergence area 3 and the flow rate of the lubricating oil within the entire gap between the rotating shaft 2 and the bearing bush 1.

While ensuring that the viscosity of the lubricating oil remains unchanged, the present invention utilizes the slip characteristics of the fluorocarbon coating and the lubricating oil to increase the flow rate of the lubricating oil on the rotating shaft 2 and the bearing bush 1, especially the flow rate in the convergence zone 3 is significantly improved. Increase the oil film pressure, load-bearing capacity and end leakage, reduce the frictional resistance of lubricating oil flow, reduce the significant increase in frictional power consumption within the oil film, quickly take away heat, suppress the temperature rise during the high-speed operation of the bearing, and improve the resistance to high-speed rotation of the bearing. Bearing capacity, therefore the proposal of combined sliding surface spiral groove bearings not only improves the bearing capacity, but also solves the problem of controlling the temperature rise of lubricating oil during high-speed machining.

Of course, the above description is not a limitation of the present invention, and the present invention is not limited to the above examples. Changes, modifications, additions or substitutions made by those skilled in the art within the essential scope of the present invention should also fall within the scope of the present invention. protection scope of the invention.

Claims (8)

1. The combined sliding surface spiral groove bearing comprises a bearing bush and a rotating shaft, and is characterized in that the rotating shaft is arranged in the bearing bush and is in clearance fit with the bearing bush;

in the use state, the axle center of the rotating shaft is positioned below one side of the axle center of the bearing bush, and the gap between the bearing bush and the rotating shaft forms a converging area and a diverging area of oil along the rotating direction of the rotating shaft;

the inner wall of the bearing bush is sequentially provided with a plurality of oil cavities at intervals along the circumferential direction, and an oil inlet and an oil outlet are arranged in each oil cavity;

the inner walls of all the oil cavities are provided with sliding coating areas, the sliding coating areas in all the oil cavities are positioned in the convergence area, the inner walls of the oil cavities extend out along the rotation direction of the rotating shaft, and sliding coating extension areas are formed on the inner walls of the bearing bushes.

2. The combined sliding surface spiral groove bearing of claim 1, wherein the opening of the oil cavity on the inner wall of the bearing bush is parallelogram, and the bottom of the oil cavity is in an arc structure with high ends and low middle along the circumferential direction;

the oil inlet and the oil outlet are arranged at the lowest part of the bottom of the oil cavity and distributed at two ends of the oil cavity along the axial direction of the bearing bush.

3. A combined sliding surface helical groove bearing according to claim 2, wherein the side of the opening of the oil chamber near the oil outlet is inclined in the rotation direction of the rotary shaft with respect to the side of the oil inlet thereof.

4. The combination sliding surface helical groove bearing of claim 1, wherein the sliding coating area covers the bottom of the oil chamber, is biased to one side of the rotation direction of the rotation shaft from the connection position of the oil inlet and the oil outlet, and extends to the opening edge of the oil chamber.

5. A combined sliding surface helical groove bearing according to claim 1, wherein the sliding coating extension covers the inner surface of the bearing bush, the outer profile of which is right trapezoid, and the angle between the oblique side of the sliding coating extension and the rotation direction of the rotating shaft is 5 ° to 8 °.

6. The combination sliding surface helical groove bearing of claim 1, wherein there are at least two sliding coating extending areas in the converging area, the circumferential length of each sliding coating extending area decreasing in turn in the direction of rotation of the shaft from the maximum clearance between the bearing shell and the shaft to the minimum clearance;

the first sliding coating extending area is positioned in the convergence area and extends to the opening of the adjacent oil cavity along the rotating direction of the rotating shaft.

7. A combined sliding surface helical groove bearing according to claim 1 wherein the coating of the sliding coating region and the sliding coating extension region is a fluorocarbon coating.

8. The combination sliding surface helical groove bearing of claim 1, wherein said oil inlet and oil outlet are located near the ends of the oil chamber along the axial direction of the bearing shell, respectively.