Electromagnetically enabled active dynamic pressure gas bearing

Abstract

An electromagnetically enabled active dynamic pressure gas bearing is provided and includes an electromagnetic bearing and an elastic foil bearing sleeved between the electromagnetic bearing and a rotor shaft. The elastic foil bearing includes a top layer elastic foil and a bottom layer elastic foil, the top layer elastic foil is made of non-magnetic material, and a plurality of separate magnetic material areas are distributed on a surface of the top layer elastic foil.

Claims

1. An electromagnetically enabled active dynamic pressure gas bearing, comprising an electromagnetic bearing and an elastic foil bearing sleeved between the electromagnetic bearing and a rotor shaft; wherein the elastic foil bearing comprises a top layer elastic foil and a bottom layer elastic foil, and wherein the top layer elastic foil is made of non-magnetic material, and a plurality of separate magnetic material areas are distributed on a surface of the top layer elastic foil; wherein the top layer elastic foil is a flat foil and the bottom layer elastic foil is a waved foil, the flat foil is made of stainless steel band which is a non-magnetic material, and after the separate magnetic material areas are sprayed on the surface of the top layer elastic foil, the surface of the top layer elastic foil is covered by a ceramic coating.

2. The electromagnetically enabled active dynamic pressure gas bearing according to claim 1, wherein the magnetic material areas are strip-shaped magnetic material areas, the strip-shaped magnetic material areas are uniformly distributed and a length direction of the strip-shaped magnetic material areas is parallel to a direction of an axis of the rotor shaft.

3. The electromagnetically enabled active dynamic pressure gas bearing according to claim 1, wherein the magnetic material areas are dotted magnetic material areas, the dotted magnetic material areas are uniformly distributed.

4. An electromagnetically enabled active dynamic pressure gas bearing, comprising an electromagnetic bearing and an elastic foil bearing sleeved between the electromagnetic bearing and a rotor shaft; wherein the elastic foil bearing comprises a top layer elastic foil and a bottom layer elastic foil, and wherein the top layer elastic foil is made of non-magnetic material, and a plurality of separate magnetic material areas are distributed on a surface of the top layer elastic foil; wherein the electromagnetically enabled active dynamic pressure gas bearing further comprises an elastic foil bearing seat, a bearing housing and a plurality of pressure sensors; wherein the electromagnetic bearing is located between the elastic foil bearing seat and the bearing housing; the elastic foil bearing seat is configured to mount the bottom layer elastic foil; and a probe of each of the pressure sensors passes through the elastic foil bearing seat to detect a gas pressure at the bottom layer elastic foil; wherein the electromagnetically enabled active dynamic pressure gas bearing further comprises a left end cover and a right end cover; wherein the electromagnetic bearing comprises magnetic poles and coils wound on the magnetic poles; there are a plurality of the magnetic poles, the magnetic poles are mounted between the elastic foil bearing seat and the bearing housing and are uniformly distributed along a circumferential direction of the elastic foil bearing, and one end of the magnetic poles points to the axis of the rotor shaft; and the left end cover and the right end cover are located at two ends of the elastic foil bearing seat and the bearing housing and press the magnetic poles; wherein the plurality of pressure sensors are located at an intermediate portion of the elastic foil bearing and are uniformly distributed along the circumferential direction of the elastic foil bearing; and there are eight magnetic poles and each of the magnetic poles is composed of stacked silicon steel sheets.

5. The electromagnetically enabled active dynamic pressure gas bearing according to claim 4, wherein material of the elastic foil bearing seat, the left end cover and the right end cover is duralumin material.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 is a front view of an electromagnetically enabled active dynamic pressure gas bearing according to the present application;

(2) FIG. 2 is a sectional view along line A-A in FIG. 1;

(3) FIG. 3 is an enlarged view of a part B in FIG. 2;

(4) FIG. 4 is a schematic view showing an unfolded top layer foil having strip-shaped magnetic material of the electromagnetically enabled active dynamic pressure gas bearing according to the present application;

(5) FIG. 5 is a schematic view showing an unfolded top layer foil having dotted magnetic material of the electromagnetically enabled active dynamic pressure gas bearing according to the present application; and

(6) FIG. 6 is a schematic view showing a deformation of the top layer foil of the electromagnetically enabled active dynamic pressure gas bearing according to the present application.

DETAILED DESCRIPTION

(7) The technical solution of the present application is further described in conjunction with drawings of the specification.

(8) As shown in FIG. 1 and FIG. 2, an electromagnetically enabled active dynamic pressure gas bearing according to the present application includes an electromagnetic bearing 1, an elastic foil bearing 3 sleeved between the electromagnetic bearing 1 and a rotor shaft 2, an elastic foil bearing seat 4, a bearing housing 5, a pressure sensor 6, a left end cover 7 and a right end cover 8. The elastic foil bearing 3 includes a top layer elastic foil 31 and a bottom layer elastic foil 32. The top layer elastic foil 31 is made of non-magnetic material and a plurality of separate magnetic material areas are distributed on a surface of the top layer elastic foil 31.

(9) The electromagnetic bearing 1 is located between the elastic foil bearing seat 4 and the bearing housing 5, the elastic foil bearing seat 4 is configured to install the bottom layer elastic foil 32, and a probe of the pressure sensor 6 passes through the elastic foil bearing seat 4 to detect a gas pressure at the bottom layer elastic foil 32. The number of the pressure sensor 6 is eight, and the pressure sensors 6 are located at an intermediate portion of the elastic foil bearing, i.e., a gas bearing, and are uniformly distributed along a circumferential direction of the gas bearing. The pressure sensor 6 includes a pressure sensor cover 61 and a pressure sensor probe 62.

(10) The electromagnetic bearing 1 includes a magnetic pole 11 and a coil 12 wound around the magnetic pole 11, the number of the magnetic pole 11 is eight and each magnetic pole 11 is formed by stacking and pressing silicon steel sheets. The magnetic poles 11 are mounted between the elastic foil bearing seat 4 and the bearing housing 5 and are uniformly distributed along a circumferential direction of the gas bearing, and one end of the magnetic poles 11 points to an axis of the rotor shaft 2. The left end cover 7 and the right end cover 8 are located at two ends of the elastic foil bearing seat 4 and the bearing housing 5 to tightly press the magnetic poles 11.

(11) Material of the elastic foil bearing seat 4, the left end cover 7 and the right end cover 8 is non-magnetic duralumin material.

(12) As shown in FIG. 4 and FIG. 5, the magnetic material areas distributed on the surface of the top layer elastic foil 31 are strip-shaped magnetic material areas or dotted magnetic material areas, the strip-shaped magnetic material areas or the dotted magnetic material areas are uniformly distributed and a length direction of the strip-shaped magnetic material areas is parallel to that of the axis of the rotor shaft 2. If the whole top layer elastic foil 31 is covered by magnetic material, a magnetic force will be greatly increased and complexity of stress condition of a restrictor sheet will be greatly increased in a control process. If the top layer elastic foil 31 does not have sufficient flexibility, an issue of curvature varying with deformation is apt to occur.

(13) The top layer elastic foil 31 is a flat foil and the bottom layer elastic foil 32 is a waved foil. The flat foil is made of stainless steel band which is a non-magnetic material. After the plurality of the separate magnetic material areas is sprayed on the surface of the top layer elastic foil 31, the surface of the top layer elastic foil 31 is covered by a ceramic coating. The top layer elastic foil 31 may also be formed to be a plate by sintering ceramic nanometer micro mist which consists of 40% zirconia, 30% aluminium oxide and 30% magnesium aluminate.

(14) As shown in FIG. 6, a section of the rotor shaft 2 may not be an ideal circle in real life. When an out-of-roundness affects the pressure of a gas film during a rotation process, the top layer elastic foil 31 of the gas bearing moves downward and thus the pressure of a lower cavity increases and the pressure of an upper cavity decreases.

(15) After a bearing gap is increased for decreasing an accuracy of the rotor shaft, the effect to a gas film pressure and a distribution thereof from the out-of-roundness of the rotor shaft 2 is correspondingly decreases. After the dynamic pressure gas bearing, which increases the bearing gap, reaches a sufficient rotating speed, finishes a starting up and reaches a balanced state, both a bearing rigidity and a carrying capacity thereof are decreased compared with a bearing which has a smaller bearing gap. In this case, a magnetic bearing is required to be introduced to make up this point.

(16) When a loading is loaded on the rotor shaft 2 and the rotor shaft 2 gradually descends and approaches the top layer elastic foil 31, the electromagnet bearing 1 may receive a signal of increased gas pressure transmitted from the pressure sensor 6 and gets involved to work. A magnetic force is not completely and directly acted on the rotor shaft 2 by the electromagnetic bearing 1 to make the rotor shaft 2 to be suspended, but the magnetic force actively pushes up the top layer elastic foil 31 to actively increase the pressure of the lower cavity, adapt to the weight loaded on the rotor shaft 2 and automatically redistribute airflow pressures in all directions in the bearing. When the rotor shaft 2 reaches a new balance position, the electromagnet bearing 1 stops working unless a new disturbance occurs.

(17) When an external shock disturbance occurs, the rotor shaft 2 may rapidly approach the top layer elastic foil 31. If the gas bearing, cannot timely make a response at this moment, it is possible to cause that a flow speed of a partial gas approaches or even reaches the speed of sound because the gap is too small in an instant, thereby causing a shock wave to generate a phenomenon of gas hammer self-excitation. The occurrence of the shock wave will cause the flow of partial gas to generate a disturbance and a chaos. When the fluid speed changes between the speed of sound and the subsonic speed, the pressure thereof significantly decreases in a step manner. In this case, the principle of hydrodynamic force is opposite to that in a usual case, that is, the flow gap between a surface of the rotor shaft 2 and the top layer elastic foil 31 is smaller and the pressure is lower instead. In this case, the top layer elastic foil 31 is required to actively avoid the surface of the rotor shaft 2 and create a larger flow gap to keep the gas flow speed in a subsonic speed range as far as possible and to maintain a normal flow pressure.

(18) In such a working condition that the compensation capability of the gas bearing is beyond, if the gas bearing is wished to keep normally working, an external force is required to be introduced to readjust the relative position between the top layer elastic foil 31 and the rotor shaft 2. It is equivalent to use the action of the electromagnetic bearing 1 to forcedly open a gap between the rotor shaft 2 and the top layer elastic foil 31 at a narrow place. At this time, the magnetic poles at two ends in this direction should be controlled to be excited by the same polarity. An attraction is generated in a direction of a small gap to draw back the top layer elastic foil 31 and an attraction is generated in a direction of a large gap to draw back the rotor shaft 2. A magnetic force difference is generated by using an operating distance difference of magnetic forces at two ends, to pull the rotor shaft 2 to recover a normal gap between the rotor shaft 2 and the top layer elastic foil 31 and thus make the airflow and working condition of the gas bearing, to return to a balanced state again. If the same situation happens to a traditional gas-magnetic hybrid bearing which has a low process requirement (a large gap), since the gas bearing loses the self-adaptive and adjustable capability, the rotor will be continually pressed toward one side of a shaft sleeve by an air pressure difference but the electromagnetic bearing will generate a magnetic force and try to pull the rotor. Thus, mutual confrontation is formed between the two bearings. In this case, the gas bearing often has a stronger bearing rigidity and thus it causes a series of problems which seriously affect the working and performance of the bearings, such as the two sets of bearing systems continually saw away and generate sharp shakings or they are locked in a stalemate and thus the rotor cannot return to a normal working condition, and they are always rigid to each other and so on.

(19) A set of displacement sensors 9 (shown in FIG. 6) are still required to be retained in the dynamic pressure gas bearing according to the present application. The dynamic pressure gas bearing does not have any assistance of external gas sources and it has to rely on its own structure to generate a gas source. Therefore, the gas-magnetic hybrid bearing based on such dynamic pressure gas bearing usually needs to retain the capability of 0 start and hot shutdown. When the rotor has a very low rotating speed or about to stop, the gas source pressure of the gas bearing, is very low and cannot completely bear the weight of the rotor, and serious abrasions are apt to occur at this time. Therefore, the displacement sensor is required to get involved at this period, the rotor is temporarily held up by actively using the electromagnetic bearing 1 and then the rotor is switched to other working conditions when the rotating speed of the rotor increases till it meets a loading condition of the gas bearing, or decreases to be close to an ideal working condition that a stop has been finished.

(20) It may be appreciated that, the above embodiments are only for illustrating the principle of the present disclosure, but the present disclosure is not limited herein. A person skilled in the art may make further modifications and improvements without departing from the principle of the present disclosure, and these modifications and improvements shall also fall within the scope of the present disclosure.