CN211288474U

CN211288474U - Hydrostatic bearing working in high G value centrifugal field

Info

Publication number: CN211288474U
Application number: CN202020023882.4U
Authority: CN
Inventors: 吕磊; 陈磊; 黎启胜; 宋琼; 舒杨
Original assignee: General Engineering Research Institute China Academy of Engineering Physics
Current assignee: General Engineering Research Institute China Academy of Engineering Physics
Priority date: 2020-01-07
Filing date: 2020-01-07
Publication date: 2020-08-18
Anticipated expiration: 2030-01-07

Abstract

The utility model discloses a hydrostatic bearing working in a high G value centrifugal field, wherein a hydrostatic bearing main body is connected with a main shaft at the hydrostatic bearing through a dynamic sealing structure; a back pressure valve is arranged at an oil return interface of the hydrostatic bearing; the oil inlet pressure is P1, the oil return pressure is P2, the pressure set by the backpressure valve is P3, the maximum pressure which can be borne by the dynamic seal is P4, the pressure of a centrifugal field at the position of the hydrostatic bearing on hydraulic oil is P5, P3> P5, P2> P3, P4> P2 and P1> P3; the utility model adopts the main shaft rotary dynamic seal and the back pressure valve at the oil return interface, so that a relatively closed and sealed internal oil storage space is formed inside the hydrostatic bearing; compared with the traditional technology, the bearing capacity of the bearing is far greater than that of a gas hydrostatic bearing; the back pressure valve is used for controlling and adjusting the hydraulic oil pressure in the bearing oil storage space, so that oil return of the hydrostatic bearing working in a centrifugal field is realized.

Description

Hydrostatic bearing working in high G value centrifugal field

Technical Field

The utility model belongs to the technical field of centrifuge, concretely relates to hydrostatic bearing who works under high G value centrifugal field.

Background

Under certain conditions or special circumstances, it is desirable to mount a hydrostatic bearing at the end of the rotor arm or at the outer diameter of the rotor disk of an arm or disk centrifuge, with its axis parallel to the axis of the centrifuge's main shaft, as shown in FIG. 1.

In the conventional technology, the hydrostatic bearing working under the centrifugal field usually adopts a gas hydrostatic bearing instead of a liquid hydrostatic bearing. The gas hydrostatic bearing has the advantages that the gas hydrostatic bearing needs to supply clean air with certain pressure to the bearing, the bearing can work normally, and after the gas leaks out of the bearing, the air does not pollute the environment, and the gas does not need to be circulated in the bearing work, so that the gas hydrostatic bearing does not need to be recycled in a centrifugal field. However, aerostatic bearings have the disadvantage that they have a low load capacity due to the high compressibility of the gas. Generally, the hydrostatic bearing has smaller compressibility by using hydraulic oil as a bearing working medium, and the bearing can work under higher oil supply pressure, so the bearing capacity of the hydrostatic bearing is higher than that of the aerostatic bearing. However, the hydrostatic bearing has the disadvantage that the working medium, i.e. the hydraulic oil, needs to be recycled. When the hydrostatic bearing is applied to a centrifugal machine and works in a centrifugal field, the hydraulic oil circulation of the hydrostatic bearing becomes a restriction on the application. Therefore, hydrostatic bearings used in centrifugal fields are less visible at present, and especially when the bearings are operated in centrifugal fields with high G-values (i.e. where the acceleration values of the centrifugal field are high), the hydraulic oil cannot be circulated by means of a return pump at the ground due to the centrifugal field.

Aerostatic bearings have applications in centrifugal fields because they do not require the recovery of circulating clean air. However, the bearing load capacity of the aerostatic bearing applied in the centrifugal field is low due to the reason that the bearing vibration is easily caused by the high gas supply pressure due to the high compressibility of the gas.

The hydrostatic bearing needs to recycle the working medium hydraulic oil. In a centrifugal field, however, the recovery of the hydraulic oil needs to be against the centrifugal force of the centrifugal field on the hydraulic oil. Since this problem is difficult to solve, the use of hydrostatic bearings in centrifugal fields has not been seen.

To solve the above problems, the inventor developed a hydrostatic bearing operating in a centrifugal field with a high G-value.

Disclosure of Invention

The object of the present invention is to provide a hydrostatic bearing that operates in a high G-value centrifugal field in order to solve the above-mentioned problems.

The utility model discloses a following technical scheme realizes above-mentioned purpose:

a hydrostatic bearing working in a high G value centrifugal field is characterized in that a hydrostatic bearing main body is connected with a main shaft at the hydrostatic bearing through a dynamic sealing structure;

a back pressure valve is arranged at an oil return interface of the hydrostatic bearing;

the oil inlet pressure is P1, the oil return pressure is P2, the pressure set by the backpressure valve is P3, the maximum pressure which can be borne by the dynamic seal is P4, the pressure of a centrifugal field at the position where the hydrostatic bearing is located on hydraulic oil is P5, P3> P5, P2> P3, P4> P2 and P1> P3.

The beneficial effects of the utility model reside in that:

the utility model relates to a hydrostatic bearing which works in a high G value centrifugal field;

1. the main shaft rotary dynamic seal is adopted, and the oil return interface backpressure valve is adopted, so that a relatively closed and sealed internal oil storage space is formed inside the hydrostatic bearing; compared with the traditional technology, the bearing capacity of the bearing is far greater than that of a gas hydrostatic bearing;

2. the back pressure valve is used for controlling and adjusting the hydraulic oil pressure in the bearing oil storage space, so that oil return of the hydrostatic bearing working in a centrifugal field is realized.

Drawings

FIG. 1 is a schematic diagram of a hydrostatic bearing operating in a centrifugal field;

FIG. 2 is a schematic view of the working principle of a hydrostatic bearing in a centrifugal field;

fig. 3 is a schematic structural diagram of the present invention.

In the figure: 1-centrifuge main shaft; 2-rotating arm; 3-hydrostatic bearings; 31-back pressure valve; 32-dynamic sealing structure; 4-a ground hydraulic station; 5-rotating joint.

Detailed Description

The present invention will be further explained with reference to the accompanying drawings:

examples, as shown in FIGS. 1-3; (rotating arm 2 is shown in FIG. 1)

A hydrostatic bearing 3 working in a high G value centrifugal field, the main body of the hydrostatic bearing 3 is connected with a main shaft of the hydrostatic bearing 3 through a dynamic seal structure 32;

a back pressure valve 31 is arranged at an oil return interface of the hydrostatic bearing 3;

the oil inlet pressure is P1, the oil return pressure is P2, the pressure of the backpressure valve 31 is P3, the maximum pressure which can be borne by the dynamic seal is P4, the pressure of a centrifugal field at the position of the hydrostatic bearing 3 on hydraulic oil is P5, P3> P5, P2> P3, P4> P2 and P1> P3. There is generally no direct association between P1 and P4, but P4> P1 is usually required to be satisfied. Typically, P1> P2. The P3 pressure value, once set, does not change during operation.

The principle of a hydrostatic bearing 3 system operating in a high G-value centrifugal field is shown in fig. 2. The hydrostatic bearing 3 adopts a rotary dynamic sealing structure 32 which can seal the higher internal hydraulic oil pressure at the bearing outlets at the upper end and the lower end of the hydrostatic main shaft; an oil inlet and an oil return port of the hydrostatic bearing 3 are respectively communicated with an oil supply pipeline and an oil return pipeline. The oil supply pipeline and the oil return pipeline are connected with an oil supply interface and an oil return interface of a ground hydraulic station 4 arranged on the ground through a rotary joint 5 of the centrifuge main shaft 1.

When the centrifugal machine works, hydraulic oil with pressure is supplied to the static pressure bearing of the centrifugal field by the hydraulic station, and the oil return pump of the hydraulic station is started to pump and recover the hydraulic oil. At the moment, pressure oil enters the inside of the bearing through a bearing inlet, and because the backpressure valve 31 is installed at a bearing oil return connector and dynamic seals are installed at two ends of the main shaft, hydraulic oil is gradually accumulated in the bearing to discharge internal air. When the bearing is filled with hydraulic oil, the pressure of the hydraulic oil is gradually increased but is not higher than the oil supply pressure of the hydraulic station. When the pressure of the hydraulic oil accumulated in the bearing is higher than the set pressure of the backpressure valve 31 at the oil return opening of the bearing, the backpressure valve 31 is opened, and the hydraulic oil naturally resists the acting force formed by the centrifugal field on the hydraulic oil under the action of the pressure and returns to the ground hydraulic station 4 along the communicated oil return pipeline.

As shown in fig. 3, the oil inlet pressure P1, the oil return pressure P2, the back pressure valve 31 set pressure P3, the maximum pressure P4 that the dynamic seal structure 32 can bear, and the pressure P5 that the centrifugal field at the position of the bearing generates to the hydraulic oil. The pressure P1 supplied to the bearing will be reduced after the bearing is operated, and air will be exhausted from the bearing and gradually accumulated. At this time, since the interior of the bearing is not filled with hydraulic oil, the pressure inside the bearing at this time is equal to the pressure P5 of the centrifugal field to the hydraulic oil. The backpressure valve 31 pressure P3> centrifugal field pressure P5 is artificially set, and the backpressure valve 31 is closed at the time. As the hydraulic oil accumulates, when full, the pressure of the hydraulic oil inside the bearing gradually increases as the oil inlet pressure P1 is typically greater than P3 or P5. When the oil pressure is > P5, < P3, the hydraulic oil cannot flow back because the back pressure valve 31 is not yet opened, and the pressure will continue to increase. When the pressure of the oil in the bearing is > P3, the back pressure valve 31 is opened, which is the return pressure P2. Since P2> P3, and more > P5, the pressure of the returning hydraulic oil can resist the action of the centrifugal field, thereby forming a return flow. Meanwhile, the oil return pressure P2< the dynamic seal pressure P4, and hydraulic oil cannot leak from the rotary dynamic seal position of the bearing main shaft. After the pressure relation of each position of the bearing is met, the bearing can work continuously, and oil inlet and oil return are continuous.

When the back pressure valve 31 is of a pressure-adjustable type, the back pressure is controllable. When the hydrostatic bearing 3 works in a centrifugal field with a high G value, the pressure P3 of the backpressure valve 31 is increased, the pressure P3> the pressure P5 of the centrifugal field is met, and meanwhile, the pressure correlation relation of the rest parts is established. The hydrostatic bearing 3 can be adapted and operated in this centrifugal field. The proper pressure P3 of the back pressure valve 31 can improve the oil return efficiency of the bearing, reduce the oil inlet pressure P1 and reduce the design difficulty of dynamic seal pressure P4.

The foregoing illustrates and describes the principles, general features, and advantages of the present invention. It will be understood by those skilled in the art that the present invention is not limited to the above embodiments, and that the foregoing embodiments and descriptions are provided only to illustrate the principles of the present invention without departing from the spirit and scope of the present invention. The scope of the invention is defined by the appended claims and equivalents thereof.

Claims

1. A hydrostatic bearing working in a high G value centrifugal field is characterized in that a hydrostatic bearing main body is connected with a main shaft of the hydrostatic bearing through a dynamic sealing structure;