CN108869541B

CN108869541B - Radial bearing, rotor system and control method of radial bearing

Info

Publication number: CN108869541B
Application number: CN201810031423.8A
Authority: CN
Inventors: 靳普
Original assignee: Liu Muhua
Current assignee: Liu Muhua
Priority date: 2018-01-12
Filing date: 2018-01-12
Publication date: 2024-04-02
Anticipated expiration: 2038-01-12
Also published as: WO2019137025A1; CN108869541A

Abstract

The invention provides a radial bearing, a rotor system and a control method of the radial bearing, wherein the radial bearing comprises the following components: the magnetic bearing is sleeved on the rotating shaft, and a plurality of magnetic components are arranged on the magnetic bearing along the circumferential direction; dynamic pressure generating grooves are formed in the side wall, facing the rotating shaft, of the magnetic bearing or in the circumferential surface, facing the rotating shaft, of the magnetic bearing; the magnetic bearing and the rotating shaft are provided with a bearing gap, and the rotating shaft can move in the radial direction of the rotating shaft under the action of magnetic force of the magnetic components. According to the invention, the radial bearing is provided with the bearing gap and the magnetic bearing, so that the radial bearing forms a gas-magnetic hybrid radial bearing, and the gas bearing and the magnetic bearing can work cooperatively, so that the dynamic performance and stability of the radial bearing in a high-speed running state can be improved.

Description

Radial bearing, rotor system and control method of radial bearing

Technical Field

The invention relates to the technical field of bearings, in particular to a radial bearing, a rotor system and a control method of the radial bearing.

Background

The gas turbine mainly comprises a compressor, a combustion chamber and a turbine. The air enters the compressor and is compressed into high-temperature high-pressure air, and then the air is supplied to the combustion chamber for mixed combustion with fuel, and the generated high-temperature high-pressure gas expands in the turbine to do work. When the rotor rotates at high speed, the rotor receives a force in a radial direction. In order to limit the radial movement of the shaft, radial bearings are required to be installed in the rotor system. The conventional radial bearings are all common contact bearings, and as the rotation speed of the rotor is increased, especially when the rotation speed of the rotor exceeds 40000 revolutions per minute, the common contact bearings cannot meet the requirement of the working rotation speed due to larger mechanical abrasion, so that the non-contact bearings are needed to replace the contact bearings.

In the prior art, non-contact bearings generally include magnetic bearings and air bearings. However, the magnetic bearing has the problems of too large energy consumption, heat generation and the like when being opened for a long time; and when the surface linear speed of the air bearing approaches or exceeds the sonic speed, shock waves can be generated, so that the bearing is unstable, and even catastrophic results such as shaft collision and the like are generated. It can be seen that both of the above two non-contact bearings cannot be applied to a high-speed gas turbine or a gas turbine generator set.

It is therefore desirable to provide a new radial bearing, a rotor system and a control method for the radial bearing to solve the above-mentioned problems.

Disclosure of Invention

The invention provides a radial bearing, a rotor system and a control method of the radial bearing, so as to solve the problems.

In a first aspect, the present invention provides a radial bearing for mounting on a rotating shaft, the radial bearing comprising:

the magnetic bearing is sleeved on the rotating shaft, and a plurality of magnetic components are arranged on the magnetic bearing along the circumferential direction;

dynamic pressure generating grooves are formed in the side wall, facing the rotating shaft, of the magnetic bearing or in the circumferential surface, facing the rotating shaft, of the magnetic bearing;

the magnetic bearing and the rotating shaft are provided with a bearing gap, and the rotating shaft can move in the radial direction of the rotating shaft under the action of magnetic force of the magnetic components.

Optionally, the magnetic bearing includes:

the magnetic bearing seat is sleeved on the rotating shaft, a plurality of accommodating grooves are formed in the magnetic bearing seat along the circumferential direction, the plurality of magnetic components are arranged in the accommodating grooves, and the magnetic poles of the plurality of magnetic components face the rotating shaft;

the bearing shell is sleeved outside the magnetic bearing seat;

The bearing sleeve is sleeved between the magnetic bearing seat and the rotating shaft;

the first end cover and the second end cover are respectively arranged at two ends of the bearing shell;

the bearing sleeve, the first end cover and the second end cover are matched, and the magnetic components are fixed on the magnetic bearing seat.

Optionally, the plurality of magnetic components include a plurality of permanent magnets, and the plurality of permanent magnets are circumferentially arranged on the magnetic bearing;

or, the plurality of magnetic components include a plurality of electromagnets, the plurality of electromagnets are circumferentially arranged on the magnetic bearing, and each of the plurality of electromagnets includes a magnetic core arranged on the magnetic bearing and a coil wound on the magnetic core.

Optionally, the dynamic pressure generating grooves are arranged in a matrix.

Optionally, the dynamic pressure generating grooves are V-shaped grooves arranged continuously or at intervals.

Optionally, the magnetic bearing is further provided with a static pressure air inlet orifice, one end of the static pressure air inlet orifice is communicated with the bearing gap, and the other end of the static pressure air inlet orifice is connected with an external air source and used for conveying the external air source into the bearing gap.

Optionally, the static pressure air inlet orifice is divided into at least two branches in the magnetic bearing and communicated into the bearing gap.

Optionally, the radial bearing further includes a plurality of sensors disposed at intervals along a circumferential direction of the magnetic bearing, where the plurality of sensors are any one or a combination of more of the following:

a displacement sensor for detecting the position of the rotating shaft;

a pressure sensor for detecting a gas film pressure at the bearing gap;

a speed sensor for detecting the rotation speed of the rotating shaft;

and the acceleration sensor is used for detecting the rotation acceleration of the rotating shaft.

Optionally, each sensor of the plurality of sensors includes a sensor cover and a sensor probe, a first end of the sensor probe is connected with the sensor cover, the sensor cover is fixed on the magnetic bearing, and a through hole for the sensor probe to pass through is formed in the magnetic bearing; the second end of the sensor probe penetrates through the through hole in the magnetic bearing and extends to the bearing gap, and the second end of the sensor probe is flush with one side, close to the rotating shaft, of the magnetic bearing.

In a second aspect, the present invention provides a rotor system comprising a rotating shaft and at least two radial bearings, both of which are non-contact bearings;

Wherein at least one of the at least two radial bearings is a radial bearing of any one of the first aspects.

Optionally, the shaft body of the rotating shaft is of an integrated structure, and the rotating shaft is horizontally arranged or vertically arranged;

the rotating shaft is sequentially provided with a motor, a gas compressor and a turbine;

a thrust bearing is also arranged on the rotating shaft, and the thrust bearing is a non-contact bearing;

the thrust bearing is arranged at a preset position on one side of the turbine, which is close to the compressor, wherein the preset position is a position which can enable the center of gravity of the rotor system to be located between the two radial bearings farthest from each other in the at least two radial bearings.

the rotating shaft is provided with a motor, a gas compressor, a turbine and a thrust bearing, wherein the thrust bearing is a non-contact bearing;

the rotor system further comprises a first casing and a second casing, wherein the first casing is connected with the second casing;

the generator, the thrust bearing and the two radial bearings are arranged in the first casing, the compressor and the turbine are arranged in the second casing, and the impeller of the compressor and the impeller of the turbine are arranged in the second casing.

In a third aspect, the present invention provides a control method of a radial bearing for any one of the rotor systems of the second aspect, the plurality of magnetic components of the radial bearing being a plurality of electromagnets, the method comprising:

the magnetic bearing is started, and the rotating shaft is controlled to move in the radial direction of the rotating shaft under the action of the magnetic force of the magnetic components, so that the rotating shaft moves to a preset radial position;

after the rotating speed of the rotating shaft is accelerated to the working rotating speed, closing the magnetic bearing;

when the rotor system is stopped, the magnetic bearing is started;

and after the rotating speed of the rotating shaft is reduced to zero, closing the magnetic bearing.

In a fourth aspect, the present invention provides another control method of a radial bearing for a rotor system according to any one of the second aspects, the plurality of magnetic components of the radial bearing being a plurality of electromagnets, characterized in that the method comprises:

after the rotating speed of the rotating shaft is accelerated to a first preset value, closing the magnetic bearing;

When the rotating speed of the rotating shaft is accelerated to a first-order critical speed or a second-order critical speed, the magnetic bearing is started;

closing the magnetic bearing after the rotor system has smoothly passed the first-order critical speed or the second-order critical speed;

and during the shutdown process of the rotor system, when the rotor system is decelerated to the first-order critical speed or the second-order critical speed, the magnetic bearing is started.

After the rotor system has smoothed the first order critical speed or the second order critical speed, the magnetic bearing is turned off.

And when the rotating speed of the rotating shaft is reduced to a second preset value, starting the magnetic bearing.

Optionally, when the rotation speed of the rotating shaft accelerates or decelerates to a first order critical speed or a second order critical speed, the magnetic bearing is started, including:

when the rotating speed of the rotating shaft accelerates or decelerates to a first-order critical speed or a second-order critical speed, the magnetic bearing is controlled to be started with maximum power; or,

and when the rotating speed of the rotating shaft is accelerated or decelerated to the first-order critical speed or the second-order critical speed, controlling the magnetic bearing to be opened in a stroboscopic mode according to a preset frequency.

Optionally, the method further comprises:

when the bearing gap between the rotating shaft and the magnetic bearing is changed, the magnetic bearing is started, so that the rotating shaft moves away from the gap reducing side under the action of the magnetic force of the magnetic components;

after the rotating shaft is in the balanced radial position, the magnetic bearing is closed.

In the present invention, the radial bearing is formed into a gas-magnetic hybrid radial bearing by providing a bearing gap and a magnetic bearing in the radial bearing. Therefore, as the gas bearing and the magnetic bearing can work cooperatively, the invention can improve the dynamic performance and stability of the radial bearing, especially in a high-speed running state, and has strong disturbance resistance, thereby improving the bearing capacity of the radial bearing. It can be seen that the radial bearing of the present invention can meet the requirements of high rotational speed gas turbines or gas turbine generator sets and the like.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings that are needed in the description of the embodiments of the present invention will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

FIG. 1 is a half cross-sectional view of a radial bearing provided in accordance with a first embodiment;

FIG. 2 is a cross-sectional view of another radial bearing provided in accordance with the first embodiment;

FIG. 3 is an external view of a radial bearing provided in accordance with an embodiment I;

FIG. 4 is a schematic view of a magnetic bearing in a radial bearing according to a first embodiment;

FIG. 5 is a schematic view of a magnetic bearing seat in a radial bearing according to an embodiment;

fig. 6 is one of schematic structural views of a radial bearing provided in the first embodiment in which dynamic pressure generating grooves are provided on a bearing housing;

FIG. 7 is a second schematic view of a radial bearing according to the first embodiment, wherein dynamic pressure generating grooves are provided in a bearing housing;

fig. 8 is a schematic view of a radial bearing provided in the first embodiment in which dynamic pressure generating grooves are provided on a rotating shaft;

fig. 9 is a schematic structural view of a rotor system according to a second embodiment;

FIG. 10 is a schematic view of a rotor system according to a third embodiment;

FIG. 11 is a schematic view of a rotor system according to a fourth embodiment;

FIG. 12 is a schematic view of another rotor system according to the fourth embodiment;

fig. 13 is a schematic view of a structure in which a locking device is provided in a rotor system according to a fifth embodiment;

FIG. 14 is a schematic view of another embodiment of a locking device in a rotor system;

FIG. 15 is a schematic view of the structure in the direction C-C in FIG. 14;

FIG. 16 is a schematic view of a structure for coating a wear-resistant coating on a rotating shaft according to a sixth embodiment;

FIG. 17 is a flow chart of a control method for a radial bearing according to a seventh embodiment;

FIG. 18 is a flow chart of another method of controlling a radial bearing provided in accordance with the seventh embodiment;

FIG. 19 is a schematic view of a thrust bearing according to an eighth embodiment;

FIG. 20 is a schematic view showing the structure of a magnetic bearing in a thrust bearing according to an eighth embodiment;

FIG. 21 is a schematic view showing the structure of a magnetic bearing seat in a thrust bearing according to an eighth embodiment;

FIG. 22 is a schematic view showing the structure of a first foil in a thrust bearing according to an eighth embodiment;

FIG. 23 is a schematic structural view of a thrust bearing provided in accordance with a ninth embodiment;

FIG. 24 is a schematic view showing the structure of a magnetic bearing in a thrust bearing according to a ninth embodiment;

FIG. 25 is a schematic view showing the structure of a magnetic bearing seat in a thrust bearing according to a ninth embodiment;

fig. 26 is one of schematic structural views of a thrust bearing in which dynamic pressure generating grooves are provided on a thrust disk in accordance with a ninth embodiment;

fig. 27 is a second schematic view of a structure in which dynamic pressure generating grooves are provided on a thrust disk in a thrust bearing provided in the ninth embodiment;

Fig. 28 is one of schematic structural views of a thrust bearing provided in the ninth embodiment in which dynamic pressure generating grooves are provided on a pressing ring;

fig. 29 is a second schematic view of a structure in which dynamic pressure generating grooves are provided in a pressure ring in a thrust bearing according to a ninth embodiment.

Detailed Description

The following description of the embodiments of the present invention will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are some, but not all embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.

As shown in fig. 1 to 8, a radial bearing 600 for mounting on a rotating shaft 100, the radial bearing 600 comprising:

the magnetic bearing 6201 is sleeved on the rotating shaft 100, and a plurality of magnetic components are arranged on the magnetic bearing 6201 along the circumferential direction;

dynamic pressure generating grooves 6202 are provided on a side wall of the magnetic bearing 6201 facing the rotating shaft 100, or on a circumferential surface of the rotating shaft 100 facing the magnetic bearing 6201;

wherein, there is a bearing gap 6203 between the magnetic bearing 6201 and the rotating shaft 100, and the rotating shaft 100 is movable in a radial direction of the rotating shaft 100 by magnetic forces of the plurality of magnetic members.

In the embodiment of the invention, the radial bearing 600 is formed into a gas-magnetic hybrid radial bearing by arranging the bearing gap 6203 and the magnetic bearing 6201 in the radial bearing 600.

During operation, the gas bearing in the radial bearing 600 can work together with the magnetic bearing 6201, and when the radial bearing 600 is in a stable working state, the support is realized by the gas bearing; while the radial bearing 600 is in an unstable operating state, the radial bearing 600 is controlled and responded to in time by means of the magnetic bearing 6201.

Therefore, the embodiment of the invention can improve the dynamic performance and stability of the radial bearing, particularly in a high-speed running state, has strong disturbance resistance, and further improves the bearing capacity of the radial bearing. The radial bearing provided by the embodiment of the invention can meet the requirements of a high-rotation-speed gas turbine or a gas turbine power generation combined set and the like.

Because of the physical characteristics of high magnetic permeability and low eddy current loss, the rotating shaft 100 is formed by laminating a plurality of silicon steel sheets or silicon steel sheets in the preferred embodiment of the invention.

In the embodiment of the present invention, when the rotating shaft 100 rotates, the flowing gas existing in the bearing gap 6203 is pressed into the dynamic pressure generating grooves 6202, thereby generating pressure to float up the rotating shaft 100, so that the rotating shaft 100 is held contactlessly in the radial direction. Among them, the magnitude of the dynamic pressure generating grooves 6202 generating pressure varies with the angle, groove width, groove length, groove depth, groove number, and flatness of the dynamic pressure generating grooves 6202. Further, the magnitude of the pressure generated by the dynamic pressure generating grooves 6202 is also related to the rotational speed of the shaft 100 and the bearing gap 6203. The parameters of the dynamic pressure generating grooves 6202 may be designed according to the actual conditions. The dynamic pressure generating grooves 6202 may be formed on the magnetic bearing 6201 or the rotary shaft 100 by forging, rolling, etching, or punching, or the like.

Optionally, the plurality of magnetic components includes a plurality of permanent magnets disposed circumferentially on the magnetic bearing 6201;

alternatively, the plurality of magnetic members include a plurality of electromagnets circumferentially disposed on the magnetic bearing 6201, each of the plurality of electromagnets including a magnetic core 62011 disposed on the magnetic bearing 6201 and a coil 62012 wound around the magnetic core 62011.

In the embodiment of the present invention, when the radial bearing 6200 only needs the magnetic component to provide magnetic force without magnetic control, the magnetic component is preferably a permanent magnet; when the radial bearing 6200 requires both magnetic force and magnetic control by a magnetic component, the magnetic component is preferably an electromagnet.

When the magnetic member is an electromagnet, a current is supplied to the coil 62012, so that the magnetic core 62011 can generate a magnetic force. The magnitude of the current flowing into the coil 62012 is different, and the magnitude of the magnetic force generated by the magnetic core 62011 is also different; the direction in which current is supplied to the coil 62012 is different, and the magnetic poles of the core 62011 are also different.

In the preferred embodiment of the present invention, the magnetic core 62011 may be formed by laminating a plurality of silicon steel sheets or silicon steel sheets, because the silicon steel sheets or silicon steel sheets have physical characteristics of high magnetic permeability, low eddy current loss, etc.

Optionally, the magnetic bearing 6201 includes:

The magnetic bearing seat 62013 and the magnetic bearing seat 62013 are sleeved on the rotating shaft 100, the magnetic bearing seat 62013 is circumferentially provided with a plurality of accommodating grooves 62014, a plurality of magnetic components are arranged in the accommodating grooves 62014, and the magnetic poles of the magnetic components face the rotating shaft 100;

bearing housing 62015 sleeved outside magnetic bearing seat 62013;

a bearing housing 62016 sleeved between the magnetic bearing block 62013 and the rotating shaft 100;

and a first end cap 62017 and a second end cap 62018 provided at both ends of the bearing housing 62015, respectively;

wherein the bearing housing 62016, the first end cap 62017 and the second end cap 62018 cooperate to fix the plurality of magnetic components to the magnetic bearing housing 62013.

In the embodiment of the invention, by arranging the bearing sleeve 62016, the bearing gap between the magnetic core 62011 and the coil 62012 can be closed, so that stable and uniform air film pressure is formed between the bearing sleeve 62016 and the rotating shaft 100. In addition, the size of the bearing gap 6203 can be conveniently adjusted and controlled by providing bearing sleeves 62016 of different radial thicknesses.

Among them, the bearing gap 6203 between the bearing housing 62016 and the rotating shaft 100 may have a width of 5 μm to 12 μm, preferably 8 μm to 620 μm.

It should be noted that, in the case that the radial bearing of the present application is applied to a vertical rotor system, when the rotating shaft 100 is not opened, the rotating shaft 100 and the bearing sleeve 62016 are coaxially disposed, after the rotating shaft 100 is opened, the axis of the rotating shaft 100 deviates from any side of the axis of the bearing sleeve 62016, and the eccentricity epsilon is 0.3 to 0.5, so as to ensure that a wedge-shaped bearing gap 6203 can be formed between the bearing sleeve 62016 and the rotating shaft 100. As the shaft 100 rotates, gas is forced into the bearing gap 6203, creating pressure to support the load. Wherein, the eccentricity epsilon=e/(R-R), wherein e is the distance between the axis of the rotating shaft and the axis of the bearing sleeve, R is the inner diameter of the bearing sleeve, R is the inner diameter of the rotating shaft, and (R-R) is the width of the bearing gap.

In the preferred embodiment of the present invention, the magnetic bearing seat 62013 is formed by laminating a plurality of silicon steel sheets or silicon steel sheets, because the silicon steel sheets or silicon steel sheets have physical characteristics of high magnetic permeability, low eddy current loss, etc. The number of the receiving grooves 62014 may be, but is not limited to, six or eight, uniformly arranged along the circumferential direction of the magnetic bearing seat 62013. Thus, the magnetic force of the magnetic bearing 6201 can be made more uniform and stable. The plurality of magnetic members may be provided on the magnetic bearing housing 62013 in other manners, which is not limited thereto. The material of the first end cap 62017 and the second end cap 62018 may be a non-magnetic material, preferably a duralumin material. The material of the bearing housing 62016 may be a non-magnetic material, preferably a duralumin material. The material of the bearing housing 62015 may be a non-magnetic material, preferably a duralumin material.

Preferably, the first end cap 62017 and the second end cap 62018 are each provided with a boss having an outer diameter identical to an inner diameter of the bearing housing 62015, and the bosses of the first end cap 62017 and the second end cap 62018 are used to fix and compress silicon steel sheets or sheets constituting the magnetic bearing housing 62013 from both ends.

In the embodiment of the present invention, dynamic pressure generating grooves 6202 may be provided on the bearing housing 62016, and the bearing housing 62016 may be made of a stainless steel material in order to facilitate the processing of the dynamic pressure generating grooves 6202. Specifically, the dynamic pressure generating grooves 6202 may be provided in the middle portion of the shaft 100 corresponding to the circumferential surface of the bearing housing 62016, or may be provided as two-part dynamic pressure generating grooves 6202 which are symmetrically distributed on both sides of the middle portion and are independent of each other; the dynamic pressure generating grooves 6202 may be provided in the middle portion of the inner side wall of the bearing housing 62016, or may be provided as two dynamic pressure generating grooves 6202 which are symmetrically distributed at both ends of the inner side wall of the bearing housing 62016 and are independent of each other.

Alternatively, dynamic pressure generating grooves 6202 are arranged in a matrix, which is advantageous in that the gas film is more uniformly distributed in bearing gap 6203.

Alternatively, the dynamic pressure generating grooves 6202 may be V-shaped grooves arranged continuously or at intervals.

In the embodiment of the present invention, by adopting the above-mentioned arrangement manner of the dynamic pressure generating grooves 6202, the rotating shaft 100 can be held in a non-contact manner in a desired manner in the case of forward rotation or reverse rotation of the rotating shaft 100, so that the rotating shaft 100 has the advantages of high load capacity and good stability. The dynamic pressure generating grooves 6202 may be provided as herringbone grooves or grooves of other shapes in addition to V-shaped grooves.

Optionally, a static pressure air inlet orifice 6205 is further disposed on the magnetic bearing 6201, one end of the static pressure air inlet orifice 6205 is communicated with the bearing gap 6203, and the other end of the static pressure air inlet orifice 6205 is connected with an external air source for conveying the external air source into the bearing gap 6203.

In the embodiment of the present invention, by providing the above-described static pressure air intake orifice 6205, a aerostatic bearing may be formed, so that the radial bearing 600 may constitute a hybrid aerostatic-magnetic radial bearing. The circulation diameter of the static pressure air inlet orifice 6205 can be adjusted according to actual working conditions such as air quantity requirements.

Alternatively, the static pressure intake orifice 6205 is split within the magnetic bearing 6201 with at least two branches communicating into the bearing gap 6203.

In embodiments of the present invention, the static pressure air inlet orifice 6205 may pass through the first end cap 62017 or the second end cap 62018, the magnetic bearing 6201, and the bearing housing 62016 in order to communicate an external air source with the bearing gap 6203. Further, the static pressure intake orifice 6205 may be split into two or more branches that communicate to the bearing gap 6203, such that the gas film pressure within the bearing gap 6203 is more uniform. Further, an annular groove may be provided on the first end cap 62017 or the second end cap 62018, and a plurality of static pressure air intake orifices 6205 may be provided in an annular region of the magnetic bearing 6201 corresponding to the annular groove, for example, one static pressure air intake orifice 6205 may be provided in each magnetic core 62011 or in each two adjacent magnetic cores 62011. The static pressure air inlet orifice 6205 and the flow diameter of the branch can be adjusted according to actual working conditions such as air flow requirements.

Optionally, the radial bearing 600 further comprises a plurality of sensors 6204 arranged at intervals along the circumference of the magnetic bearing 6201, wherein the sensor probe of each sensor 6204 is arranged within the bearing gap 6203.

In the embodiment of the invention, by arranging the sensor 6204, parameters at the bearing gap 6203, such as the air film pressure at the bearing gap 6203, and the like, can be detected in real time. Thus, the magnetic bearing 6201 can actively control the radial bearing 6200 according to the detection result of the sensor 6204, and can achieve higher accuracy of control.

Optionally, each sensor 6204 of the plurality of sensors 6204 includes a sensor cover and a sensor probe (not shown in the figure), wherein a first end of the sensor probe is connected to the sensor cover, the sensor cover is fixed on the magnetic bearing 6201, and a through hole for the sensor probe to pass through is formed on the magnetic bearing 6201; the second end of the sensor probe passes through the through hole on the magnetic bearing 6201 and extends to the bearing gap 6203, and the second end of the sensor probe is flush with one side of the magnetic bearing 6201 close to the rotating shaft 100.

In the embodiment of the present invention, the sensor 6204 can be more stably disposed on the magnetic bearing 6201 by the structural form and the mounting manner of the sensor 6204. In addition, the second end part of the sensor probe is flush with one side, close to the rotating shaft 100, of the magnetic bearing 6201, so that on one hand, the sensor probe can be prevented from being touched by the rotating shaft 100, and the sensor probe can be protected; on the other hand, the air film in the bearing gap 6203 is not affected, and the air film in the bearing gap 6203 is prevented from being disturbed.

In embodiments of the invention, the number of sensors 6204 may be the same as the number of magnetic components. The sensor 6204 may be disposed between two adjacent magnetic members, or may be disposed through a magnetic member, which is not limited in this embodiment. Each sensor 6204 is preferably disposed in the middle of the magnetic bearing 6201.

Optionally, the plurality of sensors 6204 is any one or a combination of the following:

a displacement sensor for detecting the position of the rotation shaft 100;

a pressure sensor for detecting a gas film pressure at the bearing gap 6203;

a speed sensor for detecting the rotation speed of the rotation shaft 100;

an acceleration sensor for detecting rotational acceleration of the rotation shaft 100.

Example two

An embodiment of the present invention provides a rotor system including:

the shaft body of the rotating shaft is of an integrated structure, and the rotating shaft is horizontally arranged;

the motor, the air compressor and the turbine are sequentially arranged on the rotating shaft;

the thrust bearing and the at least two radial bearings are arranged on the rotating shaft;

In an embodiment of the present invention, at least one radial bearing of the at least two radial bearings is a radial bearing provided in the present application.

In the embodiment of the invention, the thrust bearing is a bearing for limiting the movement of the rotating shaft in the axial direction, and the radial bearing is a bearing for limiting the movement of the rotating shaft in the radial direction.

With the increase of the rotation speed of the rotor, the common electromagnetic bearing and the air bearing can not meet the requirement of the rotor with high rotation speed. Therefore, in the embodiment of the invention, in order to adapt to the development requirement of high-speed rotation of the rotor, the radial bearing can adopt a non-contact bearing.

In the embodiment of the invention, the shaft body of the rotating shaft is of an integrated structure, which is understood to be a whole shaft, or the shaft body of the rotating shaft is formed by rigidly connecting a plurality of shaft sections. Because the shaft body of the rotating shaft is of an integrated structure, the strength of the shaft body at all positions on the rotating shaft is consistent, and the setting position of the thrust bearing on the rotating shaft is not limited.

Further, in order to maintain the structural stability of the entire rotor system even at high rotation speeds, the center of gravity of the entire rotor system should be located between the two radial bearings farthest apart from each other among the at least two radial bearings. Thus, the whole rotor system forms a spindle body structure, and the stability of the whole rotor system is improved in the embodiment of the invention unlike the traditional cantilever structure. Because the setting position of the thrust bearing on the rotating shaft is not limited, in the embodiment of the invention, the setting position of the thrust bearing can be flexibly adjusted according to parameters such as the setting number of the radial bearings of the at least two radial bearings, the setting position of each radial bearing, the mass of each component in the whole rotor system (including the mass of the thrust bearing), and the like, so that the center of gravity of the whole rotor system is located between the two radial bearings farthest from each other, and preferably, the center of gravity of the whole rotor system is located on the compressor.

In the embodiment of the present invention, the rotating shaft is horizontally disposed, so it can be understood that the rotor system of the embodiment of the present invention is a horizontal rotor system, which can be applied to a horizontal unit, such as a horizontal gas turbine generator set, where the horizontal rotor system is required.

As shown in fig. 9, an embodiment of the present invention provides a rotor system, which includes a rotating shaft 100 and a thrust bearing 500, wherein a shaft body of the rotating shaft 100 is an integral structure, and the rotating shaft 100 is horizontally arranged;

the rotating shaft 100 is sequentially provided with a motor 200, a compressor 300 and a turbine 400;

the rotating shaft is also provided with a first radial bearing 600 and a second radial bearing 700, and the first radial bearing 600 and the second radial bearing 700 are non-contact bearings;

the first radial bearing 600 is disposed at a side of the motor 200 remote from the compressor 300, the second radial bearing 700 is disposed between the compressor 300 and the turbine 400, and the thrust bearing 500 is disposed between the first radial bearing 600 and the motor 200.

Currently, non-contact bearings generally include electromagnetic bearings and air bearings. However, the electromagnetic bearing has the problems of too high energy consumption, heat generation and the like when being opened for a long time; and when the surface linear speed of the air bearing approaches or exceeds the sonic speed, shock waves can be generated, so that the bearing is unstable, and even catastrophic results such as shaft collision and the like are generated.

Therefore, in order to improve the working performance of the radial bearing, in the embodiment of the present invention, the first radial bearing 600 may be a gas-magnetic hybrid radial bearing or a gas-dynamic-static-pressure hybrid radial bearing in consideration of the development requirement of the high rotation speed of the gas turbine or the gas turbine generator set. The second radial bearing 700 is close to the turbine 400, and considering that the magnetic components in the magnetic bearing cannot withstand the high temperature transmitted from the turbine 400, the second radial bearing 700 can be a gas dynamic-static pressure mixed radial bearing.

As another embodiment, the second radial bearing 700 may be a gas-magnetic hybrid radial bearing, in which the magnetic component of the second radial bearing 700 is disposed on the second radial bearing 700 in a region away from the turbine 400. That is, the area of the second radial bearing 700 near the turbine 400 is not provided with magnetic components.

To protect the magnetic components on the second radial bearing 700, this may be accomplished by reducing the heat energy radiated by the turbine 400 onto the second radial bearing 700. Specifically, a thermal barrier (not shown) is disposed on the turbine 400 on a side thereof adjacent to the second radial bearing 700. Here, the material of the insulating layer may be aerogel or other materials having good insulating properties.

In the embodiment of the present invention, the compressor 300 may be a centrifugal compressor 300, and the turbine 400 may be a centrifugal turbine; the motor 200 may be a dynamic pressure bearing motor, and a first dynamic pressure generating groove 201 may be provided at a portion of the rotating shaft 100 corresponding to a bearing of the motor 200; the motor 200 may also be a heuristic motor, such that when the rotor system is started, the motor 200 may be used as a motor to drive the rotor system to rotate; when the rotor system is started, the motor 200 can be used as a generator to realize that the rotor system drives the generator to generate electricity.

Other arrangements of the thrust bearing 500 and the radial bearing in the rotor system according to the embodiments of the present invention may be adopted, and thus the embodiments of the present invention will not be described in detail.

Example III

An embodiment of the present invention provides a rotor system including:

the rotating shaft is of an integral structure, and is vertically arranged;

In the embodiment of the invention, the thrust bearing is provided in the application.

In the embodiment of the present invention, the rotating shaft is vertically disposed, so it can be understood that the rotor system of the embodiment of the present invention is a vertical rotor system, and it can be applied to a vertical unit that needs to use a vertical rotor system, for example, a vertical gas turbine generator set.

The thrust bearing and the radial bearing are non-contact bearings, so that the rotor system can be arranged vertically. Therefore, the gravity center of the rotor system is positioned at the axle center, static deflection is not generated, and the moment generated by gravity on the axle line is zero, so that the influence of gravity on the rotation of the rotor system can be eliminated, and the stability of the rotor system can be improved. Meanwhile, as the rotor system is arranged vertically, the gravity centers of all the components are downward, and the problems caused by a cantilever shaft type structure due to the horizontal arrangement of the rotor system can be avoided.

As shown in fig. 10, an embodiment of the present invention provides a rotor system, which includes a rotating shaft 100 and a thrust bearing 500, wherein a shaft body of the rotating shaft 100 is in an integral structure, and the rotating shaft 100 is vertically arranged;

Example IV

An embodiment of the present invention provides a rotor system including:

The rotating shaft is of an integral structure, and is horizontally arranged or vertically arranged;

the motor, the air compressor, the turbine, the thrust bearing and the two radial bearings are arranged on the rotating shaft, and the two radial bearings are non-contact bearings;

the first casing is connected with the second casing;

the motor, the thrust bearing and the two radial bearings are arranged in the first casing, and the compressor and the turbine are arranged in the second casing; the impeller of the compressor and the impeller of the turbine are arranged in the second casing in an abutting manner.

With the increase of the rotation speed of the rotor, the contact bearing cannot meet the requirement of the rotor with high rotation speed due to larger mechanical abrasion. Therefore, in the embodiment of the invention, in order to adapt to the development requirement of high-speed rotation of the rotor, the radial bearings can be non-contact bearings.

In an embodiment of the present invention, the first casing and the second casing may be positioned and connected by a spigot (not shown in the drawings), wherein the thrust bearing and all radial bearings may be disposed entirely within the first casing (which may be understood as a motor casing), while the second casing (which may be understood as a gas turbine casing) need not be provided with bearings. Therefore, the machining precision of the part for arranging the bearing stator in the first casing is guaranteed, the part for connecting the bearing stator in the first casing can be finished through one-time clamping machining during assembly, and therefore the machining precision and the assembly precision of the gas turbine motor unit are reduced, the cost is reduced, and the method is suitable for engineering batch production.

In the embodiment of the invention, the rotating shaft can be horizontally arranged or vertically arranged, so that it can be understood that the rotor system of the embodiment of the invention is suitable for a horizontal type unit needing to use the rotor system, and is also suitable for a vertical type unit needing to use the rotor system, such as a horizontal gas turbine motor unit or a vertical gas turbine motor unit.

In the embodiment of the invention, the shaft body of the rotating shaft is of an integrated structure, so that the gas turbine rotor and the motor rotor are connected by adopting the coupler in the prior art. Compared with the prior art, the shaft body of the rotating shaft is of an integrated structure, and the strength of the shaft body at each position on the rotating shaft is consistent, so that the setting position of the thrust bearing on the rotating shaft is not limited.

In the embodiment of the invention, the impeller of the air compressor is arranged against the impeller of the turbine, so that the axial length in the first casing is shortened, and the stability of the whole rotor system can be further improved.

Further, to reduce the influence of the heat generated by the turbine on the efficiency of the compressor, a heat insulation layer (not shown in the figure) may be disposed on the turbine of the turbine and/or on the compressor, wherein the heat insulation layer may be aerogel or other materials with good heat insulation performance; the turbine wheel of the turbine may also be made of a material having a relatively low coefficient of thermal conductivity, for example, a ceramic material.

As shown in fig. 11, an embodiment of the present invention provides a rotor system, which includes a rotating shaft 100 and a thrust bearing 500, wherein a shaft body of the rotating shaft 100 is an integral structure, and the rotating shaft 100 is horizontally arranged;

the motor 200, the compressor 300, the turbine 400, the thrust bearing 500, the first radial bearing 600 and the second radial bearing 700 are arranged on the rotating shaft 100, and the first radial bearing 600 and the second radial bearing 700 are non-contact bearings;

and a first casing 800 and a second casing 900, the first casing 800 being connected to the second casing 900, wherein the motor 200, the thrust bearing 500, the first radial bearing 600 and the second radial bearing 700 are all disposed in the first casing 800, and the compressor

300 and the turbine 400 are both disposed within the second casing 900.

The first radial bearing 600 is disposed on a side of the motor 200 away from the second casing 900, and the second radial bearing 700 is disposed on a side of the motor 200 near the second casing 900; the thrust bearing 500 is disposed between the first radial bearing 600 and the motor 200.

Therefore, in order to improve the working performance of the thrust bearing and the radial bearing, in consideration of the development requirement of the high rotation speed of the gas turbine motor unit, in the embodiment of the invention, the first radial bearing 600 may be a gas-magnetic hybrid radial bearing or a gas-dynamic-static-pressure hybrid radial bearing; the second radial bearing 700 may be a gas-magnetic hybrid radial bearing or a gas-dynamic-static hybrid radial bearing.

Optionally, the bearing capacity of the second radial bearing 700 is greater than the bearing capacity of the first radial bearing 600.

In the embodiment of the present invention, the weight of the motor 200 and the thrust bearing 500 is generally large, and the center of gravity of the entire rotor system is biased to one side of the first radial bearing 600. In view of this, increasing the load-carrying capacity of the second radial bearing 700 helps to increase the stability of the overall rotor system.

In the embodiment of the present invention, the compressor 300 may be a centrifugal compressor 300, and the turbine of the turbine 400 may be a centrifugal turbine; the motor 200 is a dynamic pressure bearing motor, and a portion of the rotating shaft 100 corresponding to a bearing of the motor 200 may be provided with a first dynamic pressure generating groove 201.

Further, the motor 200 may also be a heuristic-integrated motor.

Thus, at the initial start-up time of the rotor system, the motor 200 may be turned on in a start-up mode to rotate the rotor system, and after the rotational speed of the rotor system is increased to a preset rotational speed, the operation mode of the motor 200 may be switched to a power generation mode.

As shown in fig. 12, an embodiment of the present invention provides another rotor system, which includes a rotating shaft 100 and a thrust bearing 500, wherein a shaft body of the rotating shaft 100 is in an integral structure, and the rotating shaft 100 is vertically arranged;

300 and the turbine 400 are both disposed within the second casing 900.

The rest can refer to the related description in fig. 11, and can achieve the same technical effects, and in order to avoid repetition, the embodiments of the present invention will not be described in detail.

Example five

When the rotor system is used on mobile equipment, such as an extended range electric automobile, the rotating shaft is in direct contact with the bearing under the condition that the rotor system does not work. During running of the automobile, the rotating shaft moves radially or axially relative to the bearing due to jolt or vibration, so that abrasion is generated between the rotating shaft and the bearing, and the precision and the service life of the bearing are further affected.

Therefore, in order to solve the above-mentioned problems, on the basis of other embodiments of the present invention, the rotor system of the embodiment of the present invention is provided with a locking device for locking the rotation shaft when the rotor system is not in operation.

In the embodiment of the present invention, the structure and the arrangement manner of the locking device are not unique, and for convenience of understanding, two embodiments of the locking device provided in the rotor system are specifically described below with reference to fig. 9.

In one embodiment, as shown in fig. 13, the locking device 110 includes a telescopic propping unit 111, a connecting rod 112 and a fixing member 113, one end of the connecting rod 112 is connected with the fixing member 113, the other end is connected with the telescopic propping unit 111, the telescopic propping unit 111 faces an end face of one end, far away from the turbine 400, of the rotating shaft 100, and the other end of the fixing member 113 is fixedly connected to a housing for mounting the rotor system of the present application.

When the rotor system is stopped, the telescopic jacking unit 111 of the locking device 110 acts and pushes the rotating shaft 100 in the axial direction of the rotating shaft 100, so that the stator of the thrust bearing 500 contacts with the thrust disc, thereby axially fixing the rotating shaft 100, and simultaneously radially fixing the rotating shaft 100 by using the friction force between the stator of the thrust bearing 500 and the thrust disc.

Further, the telescopic jacking unit 111 is provided with a jacking portion (not shown in the figure), and an end surface of the rotating shaft 100 at an end far from the turbine 400 is provided with a jacking hole (not shown in the figure). In the locked state, the tip portion is pushed into the tip hole of the rotating shaft 100, so that the rotating shaft 100 can be better fixed, and abrasion and damage to the rotating shaft 100 and the bearing in the running process of the vehicle are prevented.

In another embodiment, as shown in fig. 14 to 15, the locking device 120 may be configured as a locking device of a ferrule structure. Specifically, locking device 120 includes a telescoping unit 121 and a ferrule 122, ferrule 122 being connected to the telescoping end of telescoping unit 121. Ferrule 122 may be a semi-circular ferrule having a radius equal to or slightly greater than the radius of shaft 100, with the axis of ferrule 122 disposed parallel to the axis of shaft 100, and telescoping unit 121 mounted to a generally axially intermediate position of shaft 100 and fixedly connected to the housing in which the rotor system of the present application is mounted.

When the rotor system is stopped, the telescopic unit 121 is extended, so that the clamping sleeve 122 clamps the rotating shaft 100 and pushes the rotating shaft 100 into contact with the radial bearing, thereby radially fixing the rotating shaft 100, and simultaneously axially fixing the rotating shaft 100 by using the friction force of the radial bearing and the rotating shaft 100.

Further, the telescopic unit 121 may select a piston cylinder or a hydraulic cylinder, etc. capable of realizing telescopic control.

In this embodiment, the location of the locking device 120 on the rotating shaft 100 may not be limited, and preferably, the locking device 120 is disposed between the farthest two radial bearings in the rotor system.

It should be noted that the locking devices in fig. 13 and 14 are both based on the rotor system shown in fig. 9, and the locking devices are not described in detail herein for the rotor system according to other embodiments of the present invention.

In the embodiment of the invention, the locking device is arranged, so that the locking device can lock the rotating shaft when the rotor system does not work. In this way, the movement of the rotating shaft in the radial direction or the axial direction relative to the bearing can be prevented, and the accuracy and the service life of the bearing can be improved.

Example six

Therefore, in order to solve the above-mentioned problems, on the basis of other embodiments of the present invention, the rotor system of the embodiment of the present invention is coated with an anti-wear coating 101 at the bearing-mounting portion of the rotating shaft 100, as shown in fig. 16.

The abrasion-proof coating 101 is coated on the bearing-mounting part of the rotating shaft 100, so that the abrasion of the rotating shaft 100 and the bearing can be effectively prevented. The wear-resistant coating 101 is preferably made of a material having chemical stability, corrosion resistance, high lubrication non-tackiness, and good aging resistance, such as polytetrafluoroethylene.

It should be noted that the anti-wear coating 101 in fig. 16 is based on the rotor system arrangement shown in fig. 9, and the locking device is not described in detail herein for the rotor system according to other embodiments of the present invention.

Example seven

A method of controlling the radial bearing (wherein the magnetic component in the magnetic bearing is an electromagnet) in the rotor system according to the embodiment of the present invention will be described in detail.

As shown in fig. 17, an embodiment of the present invention provides a control method of a radial bearing, including:

s631, opening the magnetic bearing, controlling the rotating shaft to move in the radial direction of the rotating shaft under the action of the magnetic force of the magnetic components, and pushing the rotating shaft to a preset radial position.

S632, after the rotating speed of the rotating shaft is accelerated to the working rotating speed, the magnetic bearing is closed.

S633, when the rotor system is stopped, the magnetic bearing is started.

S634, after the rotating speed of the rotating shaft is reduced to zero, closing the magnetic bearing.

In the above process, after the magnetic bearing is opened, the rotating shaft is supported under the action of the magnetic bearing and reaches a preset radial position (the radial position of the rotating shaft can be detected by the displacement sensor), and a bearing gap is formed between the magnetic bearing and the rotating shaft. As the shaft rotates, the shaft begins to rotate while being lubricated by the air flow in the bearing gap to prevent wear.

The specific process for opening the magnetic bearing is as follows: and inputting a current signal with a preset value into the coil, and supporting the rotating shaft under the action of the magnetic bearing and reaching a preset radial position.

With the increasing rotation speed of the rotating shaft, when the rotation speed of the rotating shaft reaches the working rotation speed, the gas film pressure generated by the gas dynamic bearing (the gas dynamic bearing forming the radial bearing is formed by arranging a bearing gap between the magnetic bearing and the rotating shaft) of the radial bearing can stabilize the rotating shaft, and then the magnetic bearing can be closed.

When the rotor system is stopped, the rotating shaft is decelerated, in order to keep the rotating shaft stable in the whole rotor system stopping process, the magnetic bearing is started when the rotor system is stopped, and the magnetic bearing is closed until the rotating shaft is completely stopped.

As shown in fig. 18, an embodiment of the present invention further provides another control method of a radial bearing, including:

s641, opening the magnetic bearing, controlling the rotating shaft to move in the radial direction of the rotating shaft under the action of the magnetic force of the magnetic components, and pushing the rotating shaft to a preset radial position.

S642, after the rotating speed of the rotating shaft is accelerated to a first preset value, the magnetic bearing is closed.

S643, when the rotating speed of the rotating shaft is accelerated to the first-order critical speed or the second-order critical speed, the magnetic bearing is started.

Specifically, when the gas flow rate at the bearing gap between the rotating shaft and the magnetic bearing reaches a first-order critical speed or a second-order critical speed, the magnetic bearing is started until the rotating shaft is restored to the balanced radial position.

Optionally, when the rotation speed of the rotating shaft accelerates to a first-order critical speed or a second-order critical speed, starting the magnetic bearing, including:

when the rotating speed of the rotating shaft is accelerated to a first-order critical speed or a second-order critical speed, the magnetic bearing is controlled to be started at the maximum power; or,

when the rotating speed of the rotating shaft is accelerated to a first-order critical speed or a second-order critical speed, the magnetic bearing is controlled to be opened in a stroboscopic mode according to a preset frequency.

S644, after the rotor system steadily passes the first-order critical speed or the second-order critical speed, the magnetic bearing is closed.

S645, in the shutdown process of the rotor system, when the rotor system is decelerated to a first-order critical speed or a second-order critical speed, the magnetic bearing is started.

S646, after the rotor system steadily passes the first-order critical speed or the second-order critical speed, the magnetic bearing is closed.

S647, when the rotating speed of the rotating shaft is reduced to a second preset value, starting the magnetic bearing.

Specifically, when the gas flow rate at the bearing gap between the rotating shaft and the magnetic bearing is reduced to a first-order critical speed or a second-order critical speed, the magnetic bearing is started until the rotating shaft is restored to the balanced radial position.

Optionally, when the rotation speed of the rotating shaft is reduced to a first-order critical speed or a second-order critical speed, starting the magnetic bearing, including:

when the rotating speed of the rotating shaft is reduced to a first-order critical speed or a second-order critical speed, controlling the magnetic bearing to be started at the maximum power; or,

when the rotating speed of the rotating shaft is reduced to a first-order critical speed or a second-order critical speed, the magnetic bearing is controlled to be opened in a stroboscopic mode according to a preset frequency.

S648, after the rotating speed of the rotating shaft is reduced to zero, the magnetic bearing is closed.

As the rotation speed of the rotation shaft increases, when the rotation speed of the rotation shaft reaches a first preset value, for example, 5% to 30% of the rated rotation speed, the gas film pressure generated by the gas dynamic bearing (the gas dynamic bearing forming the radial bearing by setting a bearing gap between the magnetic bearing and the rotation shaft) of the radial bearing can stabilize the rotation shaft, and then the magnetic bearing can be closed.

During the shutdown of the rotor system, the rotating shaft is decelerated, and when the rotating speed of the rotating shaft is reduced to a second preset value, for example, 5% to 30% of the rated rotating speed, the magnetic bearing is started, and the magnetic bearing is closed until the rotating shaft is completely stopped.

Optionally, the method further comprises:

When a load is placed on the spindle, causing the spindle to gradually descend and approach the underlying magnetic bearing, the sensor (here, the sensor is preferably a pressure sensor) obtains a signal of an increase in air pressure, at which time the magnetic bearing needs to be involved. The magnetic bearing acts on the rotating shaft to enable the rotating shaft to suspend upwards, and when the rotating shaft reaches a new balanced radial position, the magnetic bearing stops working.

When external impact disturbance occurs, the rotating shaft can quickly approach the magnetic bearing, so that the bearing clearance between the rotating shaft and the magnetic bearing can be excessively small instantaneously, the local air flow velocity at the position where the bearing clearance is reduced approaches or even reaches the sonic velocity, and the shock wave is triggered to generate the air hammer self-excitation phenomenon. The generation of shock waves causes local gas flow disturbances and upsets, with a significant step drop in pressure as the fluid velocity changes between sonic to subsonic. In this case, it is necessary to control the magnetic members of the magnetic bearing to be alternately turned on at a preset frequency to provide a damping effect on the disturbance, thereby effectively suppressing the external disturbance. After the shaft returns to the new equilibrium radial position, the magnetic bearing stops working.

In reality, the section of the rotating shaft cannot be an ideal circle, when the out-of-roundness of the rotating shaft affects the air film pressure in the rotating process of the rotating shaft, the bearing gap between the magnetic bearing and the rotating shaft is not uniformly distributed in the radial direction, and the air film pressure is increased at the place with small gap and is reduced at the place with large gap. In order to reduce the precision of the rotating shaft, the bearing clearance can be increased, so that the influence of the out-of-roundness of the rotating shaft on the air film pressure and distribution is reduced along with the increase of the bearing clearance. However, as the bearing gap increases, the bearing capacity of the hydrodynamic bearing decreases after the rotational speed of the shaft is sufficiently high and reaches an equilibrium state. In the embodiment of the invention, the radial bearing is provided with the magnetic bearing, so that the defect of reduced bearing capacity of the gas dynamic pressure bearing can be overcome.

In the embodiment of the invention, when the radial bearing is provided with the magnetic bearing (wherein, the magnetic component in the magnetic bearing is an electromagnet) and the gas hydrostatic bearing (the magnetic bearing is provided with the hydrostatic air inlet orifice), the magnetic bearing and the gas hydrostatic bearing can be mutually standby, and when one of the magnetic bearing and the gas hydrostatic bearing fails or can not meet the opening condition, the other one can serve as the standby bearing. For example, in the case of detecting a failure of the magnetic bearing, an external air source is controlled to be turned on to perform a corresponding action instead of the magnetic bearing, thereby improving the safety and reliability of the bearing.

In the embodiment of the invention, in the case of simultaneously arranging the electromagnetic bearing and the aerostatic bearing, the following implementation manner can be included:

opening the magnetic bearing; and/or starting an external air source, and conveying air to the bearing gap through the static pressure air inlet throttle hole;

and controlling the rotating shaft to move in the radial direction of the rotating shaft under the action of magnetic force of a plurality of magnetic components and/or under the pushing action of the gas so as to enable the rotating shaft to move to a preset radial position.

Wherein, for the implementation of simultaneously opening magnetic bearing and aerostatic bearing, the bearing capacity of the radial bearing of the embodiment of the invention can be further improved.

In the process, the advantages of convenience in real-time control of the magnetic bearing are utilized, and the factors of excessive deflection of the rotating shaft, such as unbalanced mass of the rotating shaft or whirling of the rotating shaft, are actively balanced, so that the rotating shaft is fixed in a certain minimum range in the radial direction. In addition, in the acceleration process of the rotating shaft, the position (namely the linear velocity supersonic speed part) where shock waves are generated can be accurately positioned, and the magnetic bearing generates opposite force to balance the shock wave action by controlling the current magnitude, the direction and the like of the magnetic bearing. After the shock wave is stable, the control strategy of the magnetic bearing is adjusted again, and the rotating shaft is fixed in a certain minimum range in the most energy-saving mode.

In view of the above, the preferred embodiment of the present invention has the following beneficial effects:

firstly, the magnetic bearing and the gas bearing work cooperatively, so that the dynamic performance and stability of the bearing in a high-speed running state are improved, the disturbance resistance is high, and the bearing capacity of the bearing is further improved. Meanwhile, the magnetic bearing and the gas bearing adopt a nested structure, so that the structure is simplified, the integration level is high, the processing, the manufacturing and the operation are easy, and the comprehensive performance of the bearing is improved. When the rotor system is started or stopped, the magnetic bearing can be used for rotating the rotating shaft, so that the low-speed performance of the bearing is improved, the service life of the bearing is prolonged, and the safety and reliability of the bearing and the whole system can be improved.

Secondly, compared with the traditional aerostatic and static hybrid radial bearing adopting the combination of the aerostatic bearing and the aerodynamic bearing, the radial bearing provided by the embodiment of the invention has the advantage of high response speed.

And thirdly, a gas hydrostatic bearing is added to form a dynamic and static pressure-magnetic hybrid radial bearing, the bearing capacity of the bearing is further increased under the condition that the magnetic bearing and the gas hydrostatic bearing are simultaneously arranged, the magnetic bearing and the gas hydrostatic bearing can mutually reserve, and the other side can serve as a reserve bearing under the condition that one side fails or cannot meet the opening condition. For example, in the case of detecting a failure of the magnetic bearing, the control system controls the aerostatic bearing to be opened to perform corresponding actions instead of the magnetic bearing, thereby improving the safety and reliability of the bearing.

In the application, the thrust bearing in the rotor system can adopt various structural forms, and if the thrust bearing adopts a gas-magnetic hybrid thrust bearing, the thrust bearing can be a foil type gas-magnetic hybrid thrust bearing or a slot type gas-magnetic hybrid thrust bearing.

The specific structural forms of the two thrust bearings and the specific control process in the overall rotor system control are described in detail below with reference to the accompanying drawings.

Example eight

Fig. 19 to 22 are schematic structural views of a foil type air-magnetic hybrid thrust bearing according to an embodiment of the present invention.

As shown in fig. 19 to 22, the foil type air-magnetic hybrid thrust bearing 5100 includes:

the first thrust plate 5101, the first thrust plate 5101 is fixedly connected to the rotating shaft 100;

and, a first stator 5102 and a second stator 5103 penetrating through the rotating shaft 100, wherein the first stator 5102 and the second stator 5103 are respectively arranged at two opposite sides of the first thrust plate 5101;

each of the first stator 5102 and the second stator 5103 includes a first magnetic bearing 5104 and a first foil bearing 5105, a plurality of first magnetic members are provided on the first magnetic bearing 5104 in a circumferential direction, and the first foil bearing 5105 is provided with a second magnetic member capable of generating magnetic force with the plurality of first magnetic members;

the first foil bearing 5105 is disposed between the first magnetic bearing 5104 and the first thrust plate 5101, and has a first gap 5106 with the first thrust plate 5101, and the first foil bearing 5105 can move in the axial direction of the rotating shaft 100 under the action of magnetic force between the first magnetic component and the second magnetic component.

In the embodiment of the invention, the first gap 5106 and the first magnetic bearing 5104 are arranged in the thrust bearing 5100, so that the thrust bearing 5100 forms a gas-magnetic hybrid thrust bearing.

When in operation, the gas bearing in the thrust bearing 5100 can work cooperatively with the first magnetic bearing 5104, and when the thrust bearing 5100 is in a stable working state, the support is realized by the gas bearing; while the thrust bearing 5100 is in an unstable operating state, the thrust bearing 5100 is controlled and responded to in time by means of the first magnetic bearing 5104.

Therefore, the embodiment of the invention can improve the dynamic performance and stability of the thrust bearing, particularly in a high-speed running state, has strong disturbance resistance, and further improves the bearing capacity of the thrust bearing. The thrust bearing of the embodiment of the invention can meet the requirements of a high-rotation-speed rotor system, such as a gas turbine or a gas turbine power generation combined set.

In the embodiment of the present invention, the outer diameters of the first thrust plate 5101, the first stator 5102 and the second stator 5103 may be equal, and the structures of the first stator 5102 and the second stator 5103 may be identical.

When the rotor system of the embodiment of the present invention is applied to a gas turbine or a gas turbine power generation unit, the first stator 5102 and the second stator 5103 may be connected with a housing of the gas turbine through a connection member.

Optionally, the plurality of first magnetic components includes a plurality of first permanent magnets disposed circumferentially on the first magnetic bearing 5104;

Alternatively, the plurality of first magnetic members include a plurality of first electromagnets circumferentially disposed on the first magnetic bearing 5104, each of the plurality of first electromagnets including a first magnetic core 51041 disposed on the first magnetic bearing 5104 and a first coil 51042 wound around the first magnetic core.

In the embodiment of the present invention, when the foil type air-magnetic hybrid thrust bearing 5100 only needs the magnetic component to provide magnetic force without magnetic control, the first magnetic component preferably selects the first permanent magnet; when the foil type air-magnetic hybrid thrust bearing 5100 requires both magnetic force and magnetic control, the first magnetic component is preferably a first electromagnet.

When the first magnetic member is a first electromagnet, a current is applied to the first coil 51042, so that the first magnetic core 51041 generates a magnetic force. The magnitude of the current supplied to the first coil 51042 is different, and the magnitude of the magnetic force generated by the first magnetic core 51041 is also different; the direction of current flowing through the first coil 51042 is different, and the magnetic poles of the first core 51041 are also different.

In the preferred embodiment of the present invention, the first magnetic core 51041 is formed by laminating a plurality of silicon steel sheets or silicon steel sheets, because the silicon steel sheets or silicon steel sheets have physical characteristics of high magnetic permeability, low eddy current loss, etc.

Optionally, the first magnetic bearing 5104 includes:

the first magnetic bearing seat 51043, the first magnetic bearing seat 51043 is opposite to the first thrust disc 5101, a plurality of first accommodating grooves 51044 are formed in the first magnetic bearing seat 51043 along the circumferential direction, a plurality of first magnetic components are arranged in the plurality of first accommodating grooves 51044, and magnetic poles of the plurality of first magnetic components face to one side where the first foil bearing 5105 is located;

the first end cap 51045, the first end cap 51045 is disposed on a side of the first magnetic bearing block 51043 remote from the first foil bearing 5105, and cooperates with the first foil bearing 5105 to secure the first magnetic component to the first magnetic bearing block 51043.

In the preferred embodiment of the present invention, the first magnetic bearing seat 51043 is formed by laminating a plurality of silicon steel sheets or silicon steel sheets, because the silicon steel sheets or silicon steel sheets have physical characteristics of high magnetic permeability, low eddy current loss, etc. The number of the first receiving grooves 51044 may be, but is not limited to, six or eight, and are uniformly disposed along the circumferential direction of the first magnetic bearing mount 51043. In this way, the magnetic force between the first magnetic bearing block 51043 and the first foil bearing 5105 can be more uniform and stable. The plurality of first magnetic members may be provided on the first magnetic bearing seat 51043 in other manners, which is not limited thereto. The material of the first end cap 51045 may be a non-magnetic material, preferably a duralumin material.

Optionally, the first foil bearing 5105 includes:

a first foil bearing mount 51051 fixedly connected to the first magnetic bearing mount 51043;

and a first foil 51052 and a second foil 51053 disposed on the first foil bearing support 51051, the first foil 51052 being mounted on the first foil bearing support 51051, the second foil 51053 being stacked on a side of the first foil 51052 adjacent to the first thrust plate 5101;

wherein the second foil 51053 is a flat foil, and the second magnetic component is disposed on the second foil 51053, so that the second foil 51053 can move in the axial direction of the rotating shaft 100 under the magnetic force of the first magnetic component and the second magnetic component; the first foil 51052 is an elastically deformable foil capable of being elastically deformed when the second foil 51053 is moved.

The material of the first foil bearing seat 51051 is a non-magnetic material, preferably a duralumin material. The first foil 51052 is an elastically deformable foil, and the first foil 51052 is preferably a stainless steel strip that is not magnetically permeable, because the magnetically permeable material is hard and brittle and is not suitable as an elastically deformable foil.

In the embodiment of the present invention, by setting the second foil 51053 as a flat foil, it is convenient to control the distance between the second foil 51053 and the first thrust plate 5101, or, in other words, to control the size of the first gap 5106. The first foil 51052 adopts a foil capable of elastically deforming, so that on one hand, the function of connecting the second foil 51053 and the first foil bearing seat 51051 is achieved, and on the other hand, the purpose that the second foil 51053 can move relative to the first foil bearing seat 51051 along the axial direction of the rotating shaft 100 can be achieved.

Optionally, the first foil 51052 is an elastically deformable foil in a wavy shape, and the first foil 51052 is in an unsealed ring shape, and is provided with an opening, one end of the opening is a fixed end, the fixed end is fixed on the first foil bearing seat 51051, and the other end of the opening is a movable end;

wherein, when the second foil 51053 moves in the axial direction of the rotating shaft 100, the corrugations on the first foil 51052 expand or contract, and the movable end moves along the circumferential direction of the ring shape.

In the embodiment of the present invention, by providing the first foil 51052 as a waved elastically deformable foil, the second foil 51053 is pushed to move in the axial direction of the rotating shaft 100 by utilizing the stretching or shrinking characteristics of the waved patterns.

It should be noted that the shape of the first foil 51052 in the embodiment of the present invention is not limited to the wave shape, and other shapes capable of generating elastic deformation may be suitable for the first foil 51052 in the embodiment of the present invention.

Optionally, the second magnetic component comprises a first magnetic material disposed on a side surface of the second foil 51053 proximate to the first magnetic bearing 5104;

wherein the first magnetic material is distributed in a strip shape on the second foil 51053 to form a plurality of strip-shaped magnetic parts, and the plurality of strip-shaped magnetic parts are radial or annular;

Alternatively, the first magnetic means are distributed in a spot on the second foil 51053.

The material of the second foil 51053 is preferably a non-magnetic material, and after the surface of the second foil 51053 is covered with the first magnetic material, the first magnetic material may be covered with a ceramic coating. The second foil 51053 may be made by sintering ceramic nanopowders using 40% zirconia, 30% alpha alumina and 30% magnesium aluminate spinel.

If the surface of the second foil 51053 completely covers the first magnetic material, magnetic force generated between the first magnetic material and the first magnetic component is greatly increased, which easily causes deformation of the second foil 51053. In view of this, in the embodiment of the present invention, by spraying the first magnetic material on the surface of the second foil 51053, the first magnetic material is distributed in a stripe shape or a dot shape on the second foil 51053, so that the magnetic force generated between the first magnetic material and the first magnetic component can be controlled within a reasonable range, thereby avoiding the deformation of the second foil 51053 due to the excessive magnetic force.

Optionally, the foil-type air-magnetic hybrid thrust bearing 5100 further includes a first sensor 5107, and a sensor probe of the first sensor 5107 is disposed in the first gap 5106.

In the embodiment of the present invention, by providing the first sensor 5107, parameters at the first gap 5106, such as the air film pressure at the first gap 5106, etc., can be detected in real time. In this way, the first magnetic bearing 5104 can actively control the thrust bearing 5100 according to the detection result of the first sensor 5107, and control can be performed with high accuracy.

Optionally, the first sensor 5107 includes a first sensor cover 51071 and a first sensor probe 51072, a first end of the first sensor probe 51072 is connected to the first sensor cover 51071, the first sensor cover 51071 is fixed on the first magnetic bearing 5104, and through holes for the first sensor probe 51072 to pass through are provided on the first magnetic bearing 5104 and the first foil bearing 5105; the second end of the first sensor probe 51072 passes through the through holes in the first magnetic bearing 5104 and the first foil bearing 5105 and extends to the first gap 5106, and the second end of the first sensor probe 51072 is flush with the side of the first foil bearing 5105 adjacent to the first thrust plate 5101.

In the embodiment of the present invention, the first sensor 5107 can be more stably disposed on the first magnetic bearing 5104 by the structural form and the mounting manner of the first sensor 5107. The second end part of the first sensor probe 51072 is flush with one side of the first foil bearing 5105, which is close to the first thrust plate 5101, so that on one hand, the first sensor probe 51072 can be prevented from being touched by the first thrust plate 5101, and the first sensor probe 51072 can be protected; on the other hand, the air film in the first gap 5106 is not affected, and disturbance of the air film in the first gap 5106 is avoided.

Optionally, the first sensor 5107 is disposed between two adjacent first magnetic members.

In the embodiment of the present invention, at least one first sensor 5107 should be disposed on each stator, and preferably one first sensor 5107 is disposed, and the first sensor 5107 is preferably disposed between two adjacent first magnetic members.

Optionally, the first sensor 5107 is a combination of any one or more of:

a displacement sensor for detecting the position of the first thrust plate 5101;

a pressure sensor for detecting the gas film pressure at the first gap 5106;

a speed sensor for detecting the rotational speed of the first thrust disc 5101;

an acceleration sensor for detecting rotational acceleration of the first thrust plate 5101.

The following describes in detail a specific control method when the foil type air-magnetic hybrid thrust bearing (wherein the first magnetic component in the first magnetic bearing is an electromagnet) participates in the control process of the rotor system according to the embodiment of the present invention.

The embodiment of the invention provides a control method of a foil type air-magnetic hybrid thrust bearing, which comprises the following steps:

s511, opening the first magnetic bearings in the first stator and the second stator, and controlling the first thrust disc to move in the axial direction of the rotating shaft under the action of the magnetic force of the first magnetic components so that a first gap between the first thrust disc and the first foil bearing in the first stator is equal to a first gap between the first thrust disc and the first foil bearing in the second stator.

S512, after the rotating speed of the rotating shaft is accelerated to the working rotating speed, the first magnetic bearings in the first stator and the second stator are closed.

S513, when the rotor system is stopped, the first magnetic bearings in the first stator and the second stator are started.

S514, after the rotating speed of the rotating shaft is reduced to zero, the first magnetic bearings in the first stator and the second stator are closed.

In the above process, after the first magnetic bearing is opened, the first thrust disc reaches a predetermined position between the first stator and the second stator under the action of the first magnetic bearing, and the first thrust disc and the end surfaces of the first stator and the second stator have first gaps.

With the rotation of the rotating shaft, the first thrust disc starts to rotate relative to the first stator and the second stator under the condition of being lubricated by the air flow in the first gap so as to prevent abrasion. The specific process for opening the first magnetic bearing is as follows: a current signal of a predetermined value is input to the first coil, and the first thrust disk reaches a predetermined position between the first stator and the second stator by the first magnetic bearing.

Along with the increasing of the rotating speed of the rotating shaft, the rotating speed of the first thrust disc is synchronously increased, and when the rotating speed of the rotating shaft reaches the working rotating speed, the air film pressure generated by the air dynamic bearing of the thrust bearing (the air dynamic bearing forming the thrust bearing by arranging a first gap between the first thrust disc and the first stator and between the first stator and the second stator) can stabilize the first thrust disc, and then the first magnetic bearing can be closed.

When the rotor system is stopped, the first thrust disc decelerates along with the deceleration of the rotating shaft, and in order to keep the rotating shaft stable in the whole rotor system stopping process, the first magnetic bearing is started when the rotor system is stopped, and the first magnetic bearing can be closed until the first thrust disc is completely stopped.

The embodiment of the invention also provides a control method of the foil type air-magnetic hybrid thrust bearing, which comprises the following steps:

s521, opening the first magnetic bearings in the first stator and the second stator, and controlling the first thrust disk to move in the axial direction of the rotating shaft under the action of the magnetic force of the first magnetic components so that a first gap between the first thrust disk and the first foil bearing in the first stator is equal to a first gap between the first thrust disk and the first foil bearing in the second stator.

S522, after the rotating speed of the rotating shaft is accelerated to a first preset value, the first magnetic bearings in the first stator and the second stator are closed.

S523, when the rotating speed of the rotating shaft is reduced to a second preset value, starting the first magnetic bearings in the first stator and the second stator.

S524, after the rotating speed of the rotating shaft is reduced to zero, the first magnetic bearings in the first stator and the second stator are closed.

With the increasing rotation speed of the rotating shaft, the rotation speed of the first thrust disc is synchronously increased, and when the rotation speed of the rotating shaft reaches a first preset value, for example, 5-30% of the rated rotation speed, the air film pressure generated by the air dynamic bearing of the thrust bearing (the air dynamic bearing forming the foil type air magnetic hybrid thrust bearing is formed by arranging a first gap between the first thrust disc and the first stator and between the first stator and the second stator) can stabilize the first thrust disc, and then the first magnetic bearing can be closed.

During the shutdown of the rotor system, the first thrust disk is decelerated along with the deceleration of the rotating shaft, and when the rotating speed of the rotating shaft is lower than a second preset value, for example, 5-30% of the rated rotating speed, the first magnetic bearing is started, and the first magnetic bearing can be closed until the first thrust disk is completely stopped.

Optionally, the method further comprises:

When the load is applied to the first thrust disc, the first thrust disc moves in the axial direction of the rotating shaft under the action of the load, and a first gap between the first thrust disc and a first foil bearing in the first stator is not equal to a first gap between the thrust disc and a first foil bearing in the second stator, the first magnetic bearings in the first stator and the second stator are started;

the first magnetic bearings in the first stator and the second stator are closed when the first gap between the first thrust disc and the first foil bearing in the first stator is equal to the first gap between the first thrust disc and the first foil bearing in the second stator.

When a load is placed on the first thrust disc, such that the first gap between the first thrust disc and the first foil bearing of the first stator or the second stator becomes smaller and approaches the first foil bearing of the side, the first sensor (here the first sensor is preferably a pressure sensor) obtains a signal of an increase in air pressure, at which time the first magnetic bearing needs to be involved. The first magnetic bearing does not completely and directly act on the first thrust disk to enable the first magnetic bearing to move towards the first foil bearing on the other side, but uses magnetic force to move the first foil bearing on the other side towards a direction away from the first thrust disk to enable a first gap between the first thrust disk and the first foil bearing on the other side to be improved, so that the pressure on the side where the first gap is reduced is improved, the load weight on the first thrust disk is adapted, and the air flow pressure on the two first gaps is automatically redistributed. When the first thrust disc reaches a new equilibrium position, the first magnetic bearing stops working.

Specifically, if the first gap between the first thrust disc and the first foil bearing in the first stator is smaller than the first gap between the first thrust disc and the first foil bearing in the second stator, the first foil bearing in the second stator is controlled to move in the axial direction of the rotating shaft in the direction away from the first thrust disc under the action of magnetic forces between the plurality of first magnetic components and the second magnetic component.

And if the first gap between the first thrust disc and the first foil bearing in the second stator is smaller than the first gap between the first thrust disc and the first foil bearing in the first stator, controlling the first foil bearing in the first stator to move in the axial direction of the rotating shaft in the direction away from the first thrust disc under the action of magnetic force between the plurality of first magnetic components and the second magnetic component.

Optionally, when the load is applied to the first thrust disc, the first thrust disc moves in the axial direction of the rotating shaft under the load, and the first gap between the first thrust disc and the first foil bearing in the first stator is not equal to the first gap between the thrust disc and the first foil bearing in the second stator, the first magnetic bearing in the first stator and the second stator is turned on, including:

When the load is applied to the first thrust disc, the first thrust disc moves in the axial direction of the rotating shaft under the action of the load, and a first gap between the first thrust disc and a first foil bearing in the first stator is not equal to a first gap between the thrust disc and a first foil bearing in the second stator, the first magnetic bearings in the first stator and the second stator are controlled to be opened at maximum power; or,

when the load is applied to the first thrust disc, the first thrust disc moves in the axial direction of the rotating shaft under the action of the load, and the first gap between the first thrust disc and the first foil bearing in the first stator is not equal to the first gap between the thrust disc and the first foil bearing in the second stator, the first magnetic bearings in the first stator and the second stator are controlled to be opened in a stroboscopic manner according to a preset frequency.

When external impact disturbance occurs, the first thrust disc may quickly approach a first foil bearing on a certain side, which may cause the first gap on the certain side to be excessively small instantaneously, so that the local gas flow velocity at the first gap on the certain side approaches or even reaches the sonic velocity, and the shock wave is triggered to generate the air hammer self-excitation phenomenon. The generation of shock waves causes local gas flow disturbances and upsets, with a significant step drop in pressure as the fluid velocity changes between sonic to subsonic. In this case, the side first foil bearing is required to actively "dodge" the first thrust disc, thereby increasing the side first gap to maintain the air flow velocity as far as possible in the subsonic region to maintain its normal fluid pressure. Specifically, it is necessary to control the first magnetic bearings on the first stator and the second stator simultaneously, so that the magnetic poles of the first magnetic bearings are excited with the same polarity, that is, the side with the reduced first gap generates a suction force for sucking back the side first foil bearing, and the side with the increased first gap generates a suction force for pulling back the first thrust disk. In this way, the difference of the magnetic force acting distances of the two sides is utilized to generate magnetic force difference, and the first thrust disc is pulled to enable the first gap between the first thrust disc and the first foil bearings of the two sides to be restored to be normal, so that the first thrust disc is returned to the balanced state again.

In the process, the advantages of the first magnetic bearing that the real-time control is convenient are utilized, and the factors of the unbalanced mass of the first thrust disk or the excessive deflection of the first thrust disk caused by the vortex of the first thrust disk and the like are actively balanced, so that the first thrust disk is fixed in a certain minimum range in the axial direction of the rotating shaft. In addition, in the acceleration process of the first thrust disk, the position (namely the linear velocity supersonic speed part) where the shock wave is generated can be accurately positioned, and the first magnetic bearing generates opposite force to balance the shock wave action by controlling the current magnitude, the direction and the like of the first magnetic bearing. And after the shock wave is stable, the control strategy of the first magnetic bearing is regulated again, and the first thrust disc is fixed in a certain minimum range in the most energy-saving mode.

In summary, the embodiment of the invention has the following beneficial effects:

firstly, the electromagnetic bearing and the gas bearing work cooperatively, so that the dynamic performance and stability of the bearing in a high-speed running state are improved, the disturbance resistance is high, and the bearing capacity of the bearing is further improved. Meanwhile, the electromagnetic bearing and the gas bearing adopt a parallel structure, so that the structure is simplified, the integration level is high, the processing, the manufacturing and the operation are easy, and the comprehensive performance of the bearing is improved. When the rotor system is started or stopped, the thrust disc and the stator of the bearing can rotate in the bearing clearance by using the electromagnetic bearing, so that the low-speed performance of the bearing is improved, the service life of the bearing is prolonged, and the safety and reliability of the bearing and the whole system can be improved.

Secondly, compared with the traditional aerostatic and static pressure mixed thrust bearing adopting the combination of the aerostatic pressure bearing and the aerodynamic pressure bearing, the foil type aeromagnetic mixed thrust bearing provided by the embodiment of the invention has the advantage of high response speed.

Thirdly, through setting up magnetic material on the foil, can make the foil moderate deformation through the attraction of electromagnetic bearing's magnetic pole, improve the highest pressure of lubricated air film one side in the bearing and prevent lubricated air current leakage, improve thrust disk and receive the ability that the disturbance eccentric hits the wall to bearing capacity has also been improved.

Fourthly, a pressure sensor with lower cost is adopted to collect the pressure change of the air film, and the deformation of the foil is controlled by a simple control method, so that higher rotor damping can be provided, and the stability of the rotor is improved. In addition, the control method is simple, and the processing precision requirement of the bearing is not high.

Examples ten

Fig. 23 to 29 are schematic structural views of a groove-type air-magnetic hybrid thrust bearing according to an embodiment of the present invention.

As shown in fig. 23 to 29, the groove type air-magnetic hybrid thrust bearing 5200 includes:

the second thrust plate 5201, the second thrust plate 5201 is fixedly connected to the rotating shaft 100, and the second thrust plate 5201 is provided with a third magnetic component;

And a third stator 5202 and a fourth stator 5203 penetrating the rotating shaft 100, wherein the third stator 5202 and the fourth stator 5203 are respectively disposed on two opposite sides of the second thrust disc 5201;

in the third stator 5202 and the fourth stator 5203, each stator includes a second magnetic bearing 5204, a plurality of fourth magnetic members capable of generating magnetic force with the third magnetic members are circumferentially provided on the second magnetic bearing 5204, a second gap 5206 is provided between the second magnetic bearing 5204 and the second thrust plate 5201, and the second thrust plate 5201 is capable of moving in the axial direction of the rotary shaft 100 by the magnetic force between the third magnetic members and the plurality of fourth magnetic members;

wherein, the end faces of the second thrust plate 5201 facing the third stator 5202 and the fourth stator 5203, or the end faces of the third stator 5202 and the fourth stator 5203 facing the second thrust plate 5201 are provided with second dynamic pressure generating grooves 5205.

In the embodiment of the invention, the second gap 5206 and the second magnetic bearing 5204 are arranged in the thrust bearing 5200, so that the thrust bearing 5200 forms a gas-magnetic hybrid thrust bearing.

When the thrust bearing 5200 works, the gas bearing in the thrust bearing 5200 and the second magnetic bearing 5204 can work cooperatively, and when the thrust bearing 5200 is in a stable working state, the support is realized by the gas bearing; while the thrust bearing 5200 is in an unstable working state, the thrust bearing 5200 is controlled and responded by the second magnetic bearing 5204 in time.

In the embodiment of the present invention, the outer diameters of the second thrust plate 5201, the third stator 5202 and the fourth stator 5203 may be equal, and the structures of the third stator 5202 and the fourth stator 5203 may be identical.

When the rotor system of the embodiment of the present invention is applied to a gas turbine, the third stator 5202 and the fourth stator 5203 may be connected to the casing of the gas turbine through a connection.

In the embodiment of the present invention, when the second thrust plate 5201 rotates, the flowing gas present in the second gap 5206 is pressed into the second dynamic pressure generating groove 5205, thereby generating pressure to achieve that the second thrust plate 5201 is held in a noncontact manner in the axial direction. The magnitude of the pressure generated by the second dynamic pressure generating grooves 5205 varies depending on the angle, groove width, groove length, groove depth, groove number, and flatness of the second dynamic pressure generating grooves 5205. The magnitude of the pressure generated by the second dynamic pressure generating grooves 5205 is also related to the rotational speed of the second thrust disk 5201 and the second gap 5206. The parameters of the second dynamic pressure generating grooves 5205 can be designed according to the actual conditions. The second dynamic pressure generating grooves 5205 may be formed on the third stator 5202 and the fourth stator 5203 by forging, rolling, etching, or pressing, or the second dynamic pressure generating grooves 5205 may be formed on the second thrust plate 5201 by forging, rolling, etching, or pressing, or the like.

Optionally, the plurality of fourth magnetic components includes a plurality of second permanent magnets disposed circumferentially on the second magnetic bearing 5204;

alternatively, the plurality of fourth magnetic members include a plurality of second electromagnets circumferentially disposed on the second magnetic bearing 5204, each of the plurality of second electromagnets including a second magnetic core 52041 disposed on the second magnetic bearing 5204 and a second coil 52042 wound on the second magnetic core 52041.

In the embodiment of the invention, when the groove type air-magnetic hybrid thrust bearing 5200 only needs the magnetic component to provide magnetic force without magnetic control, the fourth magnetic component is preferably a second permanent magnet; when the slot type air-magnetic hybrid thrust bearing 5200 requires both magnetic force and magnetic control, the fourth magnetic component is preferably a second electromagnet.

When the fourth magnetic member is a second electromagnet, a current is supplied to the second coil 52042, so that the second magnetic core 52041 generates a magnetic force. The magnitude of the current flowing through the second coil 52042 is different, and the magnitude of the magnetic force generated by the second magnetic core 52041 is also different; the direction of current flowing through the second coil 52042 is different, and the magnetic poles of the second core 52041 are also different.

In the preferred embodiment of the present invention, the second magnetic core 52041 may be formed by laminating a plurality of silicon steel sheets or silicon steel sheets, because the silicon steel sheets or silicon steel sheets have physical characteristics of high magnetic permeability, low eddy current loss, etc.

Optionally, the second magnetic bearing 5204 includes:

the second magnetic bearing seat 52043, the second magnetic bearing seat 52043 is opposite to the second thrust disk 5201, a plurality of second accommodating grooves 52044 are circumferentially arranged on the second magnetic bearing seat 52043, a plurality of fourth magnetic components are arranged in the plurality of second accommodating grooves 52044, and the magnetic poles of the plurality of fourth magnetic components face to one side where the second thrust disk 5201 is located;

second end cover 52045 and first clamping ring 52046, second end cover 52045 set up in the one side of second magnetic bearing frame 52043 that keeps away from second thrust disk 5201, and first clamping ring 52046 sets up in the one side of second magnetic bearing frame 52043 that is close to second thrust disk 5201, and second end cover 52045 cooperates with first clamping ring 52046, fixes a plurality of fourth magnetic component on second magnetic bearing frame 52043.

In the preferred embodiment of the present invention, the second magnetic bearing seat 52043 may be formed by stacking a plurality of silicon steel sheets or silicon steel sheets, because the silicon steel sheets or silicon steel sheets have physical characteristics of high magnetic permeability, low eddy current loss, etc. The number of the second receiving grooves 52044 may be, but is not limited to, six or eight, and is uniformly disposed along the circumferential direction of the second magnetic bearing seat 52043. In this way, the magnetic force between the second magnetic bearing 5204 and the second thrust disk 5201 can be made more uniform and stable. The plurality of fourth magnetic members may be provided on the second magnetic bearing block 52043 in other manners, which is not limited thereto. The material of the second end cap 52045 can be a non-magnetic material, preferably a duralumin material. The material of the first pressure ring 52046 can be a non-magnetic material, preferably a duralumin material.

In an embodiment of the present invention, the second dynamic pressure generating groove 5205 may be provided on the first pressure ring 52046, and the first pressure ring 52046 may be made of a stainless steel material in order to facilitate processing of the second dynamic pressure generating groove 5205.

Optionally, the third magnetic component includes a second magnetic material (not shown in the figure) disposed on an end surface of the second thrust plate 5201 facing the third stator 5202 and the fourth stator 5203;

wherein the second magnetic material is distributed in a strip shape on the second thrust plate 5201 to form a plurality of strip-shaped magnetic parts, and the plurality of strip-shaped magnetic parts are radial or annular;

alternatively, the second magnetic members are distributed in a dot shape on the second thrust plate 5201.

In the embodiment of the present invention, the second magnetic material is distributed in a stripe shape or a dot shape on the second thrust disk 5201, so that the magnetic force generated between the second magnetic material and the fourth magnetic component can be controlled within a reasonable range.

Optionally, the second dynamic pressure generating grooves 5205 are arranged radially or concentrically, which is advantageous for more uniformly distributing the air film in the second gap 5206.

Optionally, the second dynamic pressure generating groove 5205 includes a first spiral groove 52051 and a second spiral groove 52052, the first spiral groove 52051 surrounds the second spiral groove 52052, the spiral directions of the first spiral groove 52051 and the second spiral groove 52052 are opposite, and one end of the first spiral groove 52051 near the second spiral groove 52052 is connected or disconnected with one end of the second spiral groove 52052 near the first spiral groove 52051.

Wherein, the distance from the end of the first spiral groove 52051 near the second spiral groove 52052 to the axle center of the rotating shaft 100 is equal to the distance from the end of the first spiral groove 52051 near the second spiral groove 52052 to the outer peripheral edge of the third stator 5202 or the fourth stator 5203 or the second thrust plate 5201. Alternatively, the distance from the end of the second spiral groove 52052 close to the first spiral groove 52051 to the shaft center of the rotary shaft 100 is equal to the distance from the end of the second spiral groove 52052 close to the first spiral groove 52051 to the outer peripheral edge of the third stator 5202 or the fourth stator 5203 or the second thrust plate 5201.

In the embodiment of the present invention, by adopting the above-mentioned arrangement manner of the second dynamic pressure generating grooves 5205, the second thrust disc 5201 can be held in a non-contact manner in a desired manner in the case that the rotating shaft 100 rotates in the forward direction or in the reverse direction, so that the rotating shaft 100 has the advantages of high load capacity and good stability.

Optionally, in the third stator 5202 and the fourth stator 5203, a first static pressure air inlet orifice 5208 is further disposed on each stator, one end of the first static pressure air inlet orifice 5208 is communicated with the second gap 5206, and the other end of the first static pressure air inlet orifice 5208 is connected with an external air source for conveying the external air source into the second gap 5206.

In the embodiment of the present invention, by providing the first static pressure air inlet orifice 5208, a aerostatic bearing may be formed, so that the thrust bearing 5200 may form a hybrid aerostatic-magnetic thrust bearing. The flow diameter of the first static pressure air inlet orifice 5208 can be adjusted according to actual working conditions such as air flow requirements.

Optionally, in the third stator 5202 and the fourth stator 5203, a plurality of first static pressure air inlet orifices 5208 are disposed on each stator, and the plurality of first static pressure air inlet orifices 5208 are disposed at intervals along the circumferential direction of the stator.

In the embodiment of the present invention, the plurality of first static pressure air intake orifices 5208 are arranged at intervals along the circumferential direction of the stator, preferably at uniform intervals along the circumferential direction of the stator. In this way, it is advantageous to make the gas film pressure in the second gap 5206 more uniform.

Optionally, in the third stator 5202 and the fourth stator 5203, a distance from the first static pressure air intake orifice 5208 to the axial center of the rotating shaft 100 is greater than or equal to a distance from the first static pressure air intake orifice 5208 to the outer peripheral edge of the stator.

In the embodiment of the present invention, the above-mentioned first static pressure air inlet orifice 5208 is arranged in a manner that the aerostatic bearing is more stable, and if the static pressure air inlet orifice is too close to the axis of the rotating shaft 100, the air film cannot be effectively distributed over the end face of the whole second thrust disc 5201 in time, so that the rotation of the second thrust disc 5201 is not stable enough. Preferably, the distance from the first static pressure intake orifice 5208 to the axial center of the rotary shaft 100 is equal to the distance from the first static pressure intake orifice 5208 to the outer peripheral edge of the stator.

Optionally, the groove type air-magnetic hybrid thrust bearing 5200 further includes a second sensor 5207, and a sensor probe of the second sensor 5207 is disposed in the second gap 5206.

In the embodiment of the invention, by arranging the second sensor 5207, parameters at the second gap 5206, such as the air film pressure at the second gap 5206, and the like, can be detected in real time. In this way, the second magnetic bearing 5204 can actively control the thrust bearing 5200 according to the detection result of the second sensor 5207, and can achieve higher accuracy of control.

Optionally, the second sensor 5207 includes a second sensor cover 52071 and a second sensor probe 52072, a first end of the second sensor probe 52072 is connected to the second sensor cover 52071, the second sensor cover 52071 is fixed on the second magnetic bearing 5204, and a through hole for the second sensor probe 52072 to pass through is provided on the second magnetic bearing 5204; the second end of the second sensor probe 52072 passes through the through hole in the second magnetic bearing 5204 and extends to the second gap 5206, and the second end of the second sensor probe 52072 is flush with the side of the second magnetic bearing 5204 that is adjacent to the second thrust disk 5201.

In the embodiment of the present invention, the second sensor 5207 can be more stably disposed on the second magnetic bearing 5204 by the structural form and the mounting manner of the second sensor 5207. In addition, the second end of the second sensor probe 52072 is flush with the side of the second magnetic bearing 5204, which is close to the second thrust plate 5201, so that on one hand, the second sensor probe 52072 can be prevented from being touched by the second thrust plate 5201, and the second sensor probe 52072 can be protected; on the other hand, the air film in the second gap 5206 is not affected, and the air film in the second gap 5206 is prevented from being disturbed.

Optionally, the second sensor 5207 is disposed between two adjacent fourth magnetic components.

In the embodiment of the present invention, at least one second sensor 5207, preferably one second sensor 5207, should be provided on each stator, and the second sensor 5207 is preferably provided between two adjacent fourth magnetic members.

Optionally, the second sensor 5207 is a combination of any one or more of the following:

a displacement sensor for detecting the position of the second thrust plate 5201;

a pressure sensor for detecting the gas film pressure at the second gap 5206;

a speed sensor for detecting the rotational speed of the second thrust plate 5201;

and an acceleration sensor for detecting rotational acceleration of the second thrust plate 5201.

The following describes in detail a specific control method when the groove type air-magnetic hybrid thrust bearing (wherein the fourth magnetic component in the second magnetic bearing is an electromagnet) participates in the control process of the rotor system.

The embodiment of the invention provides a control method of a groove type air-magnetic hybrid thrust bearing, which comprises the following steps:

s531, opening second magnetic bearings in the third stator and the fourth stator, and controlling the second thrust disk to move in the axial direction of the rotating shaft under the action of magnetic force between the third magnetic component and the plurality of fourth magnetic components so that the difference value between a second gap between the second thrust disk and the second magnetic bearings in the third stator and a second gap between the second thrust disk and the second magnetic bearings in the fourth stator is smaller than or equal to a preset value.

S532, after the rotating speed of the rotating shaft is accelerated to the working rotating speed, the second magnetic bearings in the third stator and the fourth stator are closed.

S533, when the rotor system is stopped, the second magnetic bearings in the third stator and the fourth stator are started.

S534, after the rotating speed of the rotating shaft is reduced to zero, the second magnetic bearings in the third stator and the fourth stator are closed.

In the above process, after the second magnetic bearing is opened, the second thrust disc reaches a predetermined position between the third stator and the fourth stator under the action of the second magnetic bearing, and the second thrust disc and the end surfaces of the third stator and the fourth stator have second gaps.

With the rotation of the rotating shaft, the second thrust disc starts to rotate relative to the third stator and the fourth stator under the condition of being lubricated by the air flow in the second gap so as to prevent abrasion. The specific process of opening the second magnetic bearing is as follows: a current signal of a preset value is input to the second coil, and the second thrust disk reaches a preset position between the third stator and the fourth stator under the action of the second magnetic bearing.

Along with the increasing of the rotating speed of the rotating shaft, the rotating speed of the second thrust disc is synchronously increased, and when the rotating speed of the rotating shaft reaches the working rotating speed, the air film pressure generated by the air dynamic bearing of the thrust bearing (the air dynamic bearing forming the thrust bearing by arranging a second gap between the second thrust disc and the third stator and the fourth stator) can stabilize the second thrust disc, and then the second magnetic bearing can be closed.

When the rotor system is stopped, the second thrust disc decelerates along with the deceleration of the rotating shaft, and in order to keep the rotating shaft stable in the whole rotor system stopping process, the second magnetic bearing is started when the rotor system is stopped, and the second magnetic bearing is closed until the second thrust disc is completely stopped.

The embodiment of the invention also provides a control method of the groove type air-magnetic hybrid thrust bearing, which comprises the following steps:

s541, opening second magnetic bearings in the third stator and the fourth stator, and controlling the second thrust disk to move in the axial direction of the rotating shaft under the action of magnetic force between the third magnetic component and the plurality of fourth magnetic components, so that a difference between a second gap between the second thrust disk and the second magnetic bearings in the third stator and a second gap between the second thrust disk and the second magnetic bearings in the fourth stator is smaller than or equal to a preset value.

S542, after the rotating speed of the rotating shaft is accelerated to a first preset value, the second magnetic bearings in the third stator and the fourth stator are closed.

S543, when the rotating speed of the rotating shaft is reduced to a second preset value, starting the second magnetic bearings in the third stator and the fourth stator.

S544, after the rotating speed of the rotating shaft is reduced to zero, the second magnetic bearings in the third stator and the fourth stator are closed.

In the above process, after the second magnetic bearing is opened, the second thrust disc reaches a predetermined position between the third stator and the fourth stator under the action of the second magnetic bearing, and the second thrust disc and the end surfaces of the third stator and the fourth stator have second gaps. With the rotation of the rotating shaft, the second thrust disc starts to rotate relative to the third stator and the fourth stator under the condition of being lubricated by the air flow in the second gap so as to prevent abrasion. The specific process of opening the second magnetic bearing is as follows: a current signal of a preset value is input to the second coil, and the second thrust disk reaches a preset position between the third stator and the fourth stator under the action of the second magnetic bearing.

Along with the increasing rotation speed of the rotating shaft, the rotation speed of the second thrust disc is synchronously increased, and when the rotation speed of the rotating shaft reaches a second preset value, for example, 5-30% of the rated rotation speed, the air film pressure generated by the air dynamic bearing of the thrust bearing (the air dynamic bearing forming the groove type air-magnetic hybrid thrust bearing is formed by arranging a second gap between the second thrust disc and the third stator and the fourth stator) can stabilize the second thrust disc, and then the second magnetic bearing can be closed.

During the shutdown of the rotor system, the second thrust disk is decelerated along with the deceleration of the rotating shaft, and when the rotating speed of the rotating shaft is lower than a second preset value, for example, 5% to 30% of the rated rotating speed, the air film pressure generated by the air dynamic pressure bearing of the thrust bearing is also reduced along with the deceleration of the thrust disk, so that the second magnetic bearing needs to be started to keep the second thrust disk stable, and the second magnetic bearing can be closed until the second thrust disk is completely stopped.

Optionally, the method further comprises:

when the load is applied to the second thrust disc, the second thrust disc moves in the axial direction of the rotating shaft under the action of the load, and the difference between a second gap between the second thrust disc and a second magnetic bearing in the third stator and a second gap between the second thrust disc and a second magnetic bearing in the fourth stator is larger than a preset value, the second magnetic bearings in the third stator and the fourth stator are started;

and closing the second magnetic bearings in the third stator or the fourth stator when a difference between a second gap between the second thrust disc and the second magnetic bearings in the third stator and a second gap between the second thrust disc and the second magnetic bearings in the fourth stator is less than or equal to a predetermined value.

When a load is placed on the second thrust disk, so that the second gap between the second thrust disk and the second magnetic bearing of the third stator or the fourth stator becomes smaller to approach the second magnetic bearing on the side, the second sensor (the second sensor here is preferably a pressure sensor) obtains a signal of an increase in air pressure, at which time the second magnetic bearing needs to be involved in operation. The second magnetic bearing acts on the second thrust disk by magnetic force to move the second thrust disk to the second magnetic bearing at the other side, and the second magnetic bearing stops working after the second thrust disk reaches a new balance position.

Specifically, if the second gap between the second thrust disc and the second magnetic bearing in the third stator is smaller than the second gap between the second thrust disc and the second magnetic bearing in the fourth stator, and the difference between the second gap between the second thrust disc and the second magnetic bearing in the third stator and the second gap between the second thrust disc and the second magnetic bearing in the fourth stator is greater than a predetermined value, the second magnetic bearing in the fourth stator is controlled to enable the second thrust disc to move in the axial direction of the rotating shaft in the direction away from the fourth stator under the action of magnetic force between the third magnetic component and the plurality of fourth magnetic components.

And if the second gap between the second thrust disc and the second magnetic bearing in the fourth stator is smaller than the second gap between the second thrust disc and the second magnetic bearing in the third stator, and the difference between the second gap between the second thrust disc and the second magnetic bearing in the third stator and the second gap between the second thrust disc and the second magnetic bearing in the fourth stator is larger than a preset value, controlling the second magnetic bearing in the third stator to enable the second thrust disc to move in the axial direction of the rotating shaft in the direction far away from the third stator under the action of magnetic force between the third magnetic component and the plurality of fourth magnetic components.

Optionally, when the load is applied to the second thrust disc, the second thrust disc moves in the axial direction of the rotating shaft under the action of the load, and a difference between a second gap between the second thrust disc and the second magnetic bearing in the third stator and a second gap between the second thrust disc and the second magnetic bearing in the fourth stator is greater than a predetermined value, the second magnetic bearings in the third stator and the fourth stator are turned on, including:

when the load is applied to the second thrust disc, the second thrust disc moves in the axial direction of the rotating shaft under the action of the load, and the difference between the second gap between the second thrust disc and the second magnetic bearing in the third stator and the second gap between the second thrust disc and the second magnetic bearing in the fourth stator is larger than a preset value, the second magnetic bearing in the third stator or the fourth stator is controlled to be opened at the maximum power; or,

when the load is applied to the second thrust disc, the second thrust disc moves in the axial direction of the rotating shaft under the action of the load, and the difference between the second gap between the second thrust disc and the second magnetic bearing in the third stator and the second gap between the second thrust disc and the second magnetic bearing in the fourth stator is larger than a preset value, the second magnetic bearing in the third stator or the fourth stator is controlled to be opened in a stroboscopic mode according to preset frequency.

When external impact disturbance occurs, the second thrust disc may quickly approach to the second magnetic bearing on a certain side, and the second gap on the certain side may be excessively small instantaneously, so that the local gas flow velocity at the second gap on the certain side approaches to or even reaches to the sonic velocity, and the shock wave is triggered to generate the air hammer self-excitation phenomenon. The generation of shock waves causes local gas flow disturbances and upsets, with a significant step drop in pressure as the fluid velocity changes between sonic to subsonic. In this case, it is necessary to control the second magnetic bearings in the third stator or the fourth stator to be turned on at the maximum power, or to control the second magnetic bearings in the third stator or the fourth stator to be turned on in turn in a stroboscopic manner at a preset frequency to provide a damping effect on the disturbance, thereby effectively suppressing the external disturbance. After the second thrust disk returns to the equilibrium state, the second magnetic bearing stops operating.

In the embodiment of the present invention, when the electromagnetic bearing (the electromagnetic bearing is formed as the fourth magnetic component in the second magnetic bearing) and the hydrostatic gas bearing (the hydrostatic gas bearing is formed as the first hydrostatic gas inlet orifice provided in the third stator and the fourth stator) are simultaneously provided, the electromagnetic bearing and the hydrostatic gas bearing may be mutually spare, and when one of them fails, or the opening condition cannot be satisfied, the other may serve as a spare bearing. For example, in the case of detecting a failure of the electromagnetic bearing, the external air source is controlled to be turned on to perform a corresponding action instead of the electromagnetic bearing, thereby improving the safety and reliability of the bearing.

opening a second magnetic bearing of the third stator and the fourth stator; and/or starting an external gas source, and conveying gas to the second gap through the first static pressure inlet orifice;

and controlling the second thrust disc to move in the axial direction of the rotating shaft under the action of magnetic force between the third magnetic component and the fourth magnetic component and/or the pushing action of the gas so that the difference value between the second gap between the second thrust disc and the second magnetic bearing in the third stator and the second gap between the second thrust disc and the second magnetic bearing in the fourth stator is smaller than or equal to the preset value.

In the process, the advantages of the second magnetic bearing that the real-time control is convenient are utilized, and the factors of the unbalanced mass of the second thrust disk or excessive deflection of the second thrust disk caused by the vortex of the second thrust disk and the like are actively balanced, so that the second thrust disk is fixed in a certain minimum range in the axial direction of the rotating shaft. In addition, in the acceleration process of the second thrust disk, the position (namely the linear velocity supersonic speed part) where the shock wave is generated can be accurately positioned, and the second magnetic bearing generates opposite force to balance the shock wave action by controlling the current magnitude, the direction and the like of the second magnetic bearing. And after the shock wave is stable, the control strategy of the second magnetic bearing is regulated again, and the second thrust disc is fixed in a certain minimum range in the most energy-saving mode.

firstly, the electromagnetic bearing and the gas bearing work cooperatively, so that the dynamic performance and stability of the bearing in a high-speed running state are improved, the disturbance resistance is high, and the bearing capacity of the bearing is further improved. Meanwhile, the electromagnetic bearing and the gas bearing adopt a parallel structure, so that the structure is simplified, the integration level is high, the processing, the manufacturing and the operation are easy, and the comprehensive performance of the bearing is improved. When the rotor system is started or stopped, the thrust disc of the bearing and the stator can rotate in the second gap by using the electromagnetic bearing, so that the low-speed performance of the bearing is improved, the service life of the bearing is prolonged, and the safety and reliability of the bearing and the whole system can be improved.

Secondly, compared with the traditional aerostatic and static hybrid thrust bearing adopting the combination of the aerostatic bearing and the aerodynamic bearing, the groove type aeromagnetic hybrid thrust bearing provided by the embodiment of the invention has the advantage of high response speed.

Thirdly, the aerostatic bearing is added to form a groove type dynamic static pressure-magnetic mixed thrust bearing, under the condition that the electromagnetic bearing and the aerostatic bearing are simultaneously arranged, the bearing capacity of the bearing is further increased, the electromagnetic bearing and the aerostatic bearing can be mutually standby, and under the condition that one of the electromagnetic bearing and the aerostatic bearing fails or cannot meet the opening condition, the other can serve as a standby bearing to play the same role. For example, when a fault of the electromagnetic bearing is detected, the control system controls the aerostatic bearing to be opened to replace the electromagnetic bearing to execute corresponding actions, so that the safety and the reliability of the bearing are improved.

The foregoing is merely illustrative embodiments of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily think about variations or substitutions within the technical scope of the present invention, and the invention should be covered. Therefore, the protection scope of the invention is subject to the protection scope of the claims.

Claims

1. A method of controlling a radial bearing, the method comprising a radial bearing for mounting on a rotating shaft, the radial bearing comprising: the magnetic bearing is sleeved on the rotating shaft, and a plurality of magnetic components are arranged on the magnetic bearing along the circumferential direction;

the magnetic bearing and the rotating shaft are provided with a bearing gap, and the rotating shaft can move in the radial direction of the rotating shaft under the action of magnetic force of the magnetic components;

the control method further comprises a rotor system, wherein the rotor system comprises a rotating shaft and at least two radial bearings, and the at least two radial bearings are non-contact bearings;

The shaft body of the rotating shaft is of an integrated structure, and the rotating shaft is horizontally arranged or vertically arranged;

the thrust bearing is arranged at a preset position on one side of the turbine, which is close to the compressor, wherein the preset position is a position capable of enabling the center of gravity of the rotor system to be located between the two radial bearings farthest from each other in the at least two radial bearings;

the motor, the thrust bearing and the two radial bearings are arranged in the first casing, the air compressor and the turbine are arranged in the second casing, and an impeller of the air compressor and an impeller of the turbine are arranged in the second casing;

The plurality of magnetic components of the radial bearing are a plurality of electromagnets, and the control method of the radial bearing comprises the following steps: the magnetic bearing is started, and the rotating shaft is controlled to move in the radial direction of the rotating shaft under the action of the magnetic force of the magnetic components, so that the rotating shaft moves to a preset radial position;

during the shutdown of the rotor system, when the rotor system is decelerated to the first-order critical speed or the second-order critical speed, the magnetic bearing is started;

when the rotating speed of the rotating shaft is reduced to a second preset value, the magnetic bearing is started;

2. A control method of a radial bearing according to claim 1, wherein the magnetic bearing comprises:

the bearing shell is sleeved outside the magnetic bearing seat;

3. A control method of a radial bearing according to claim 1, wherein the plurality of magnetic members include a plurality of permanent magnets disposed circumferentially on the magnetic bearing;

4. A control method of a radial bearing according to claim 1, wherein the dynamic pressure generating grooves are arranged in a matrix.

5. The method of controlling a radial bearing according to claim 4, wherein the dynamic pressure generating grooves are V-shaped grooves arranged continuously or at intervals.

6. The control method of a radial bearing according to claim 1, wherein the magnetic bearing is further provided with a static pressure air inlet orifice, one end of the static pressure air inlet orifice is communicated with the bearing gap, and the other end of the static pressure air inlet orifice is connected with an external air source for conveying the external air source into the bearing gap.

7. The method of claim 6, wherein the static pressure inlet orifice is split within the magnetic bearing into at least two branches that communicate into the bearing gap.

8. The method of claim 1, further comprising a plurality of sensors spaced apart along the circumference of the magnetic bearing, the plurality of sensors being any one or a combination of: a displacement sensor for detecting the position of the rotating shaft;

a pressure sensor for detecting a gas film pressure at the bearing gap;

a speed sensor for detecting the rotation speed of the rotating shaft;

9. The method of claim 8, wherein each sensor of the plurality of sensors includes a sensor cover and a sensor probe, a first end of the sensor probe is connected to the sensor cover, the sensor cover is fixed to the magnetic bearing, and a through hole for the sensor probe to pass through is formed in the magnetic bearing; the second end of the sensor probe penetrates through the through hole in the magnetic bearing and extends to the bearing gap, and the second end of the sensor probe is flush with one side, close to the rotating shaft, of the magnetic bearing.

10. The control method of a radial bearing according to claim 1, wherein starting the magnetic bearing when the rotational speed of the rotating shaft is accelerated or decelerated to a first-order critical speed or a second-order critical speed, comprises: when the rotating speed of the rotating shaft accelerates or decelerates to a first-order critical speed or a second-order critical speed, the magnetic bearing is controlled to be started with maximum power; or when the rotating speed of the rotating shaft accelerates or decelerates to the first-order critical speed or the second-order critical speed or the rotating shaft is subjected to external disturbance, the magnetic bearing is controlled to be opened in a stroboscopic mode according to a preset frequency.

11. A method of controlling a radial bearing according to claim 1, further comprising: when the bearing gap between the rotating shaft and the magnetic bearing is changed, the magnetic bearing is started, so that the rotating shaft moves away from the gap reducing side under the action of the magnetic force of the magnetic components;