WO2019137024A1

WO2019137024A1 - Thrust bearing, rotor system and control method for thrust bearing

Info

Publication number: WO2019137024A1
Application number: PCT/CN2018/103411
Authority: WO
Inventors: 靳普
Original assignee: 至玥腾风科技投资集团有限公司
Priority date: 2018-01-12
Filing date: 2018-08-31
Publication date: 2019-07-18
Also published as: CN108869542B; CN108869542A

Abstract

A thrust bearing (500), a rotor system and a control method for the thrust bearing, the thrust bearing comprising: a thrust disc (5101), fixedly connected to a rotating shaft (100); and a first stator (5102) and a second stator (5103) which penetrate the rotating shaft (100), the first stator (5102) and the second stator (5103) being disposed on two opposite sides of the thrust disc respectively. Each stator comprises magnetic bearings (5104) and a foil bearing (5105), a plurality of first magnetic parts are arranged on the magnetic bearings (5104) in the circumferential direction, and second magnetic parts are arranged on the foil bearings (5105), wherein the foil bearings (5105) are disposed between the magnetic bearings (5104) and the thrust disc (5101), bearing gaps (5106) are formed between the foil bearings (5105) and the thrust disc (5101), and the foil bearings (5105) may move in the axial direction of the rotating shaft (100) under the action of magnetic force. The bearing gaps and the magnetic bearings are provided in the thrust bearing, so that the thrust bearing forms a gas and magnet hybrid thrust bearing, and the dynamic performance and the stability of the thrust bearing under a high-speed running state may be improved owing to gas bearings and the magnetic bearings being able to work cooperatively.

Description

Thrust bearing, rotor system and control method of thrust bearing

Cross-reference to related applications

The present application claims priority to Chinese Patent Application No. 20181003199, filed on Jan. 12, 2011, the entire disclosure of which is hereby incorporated by reference.

Technical field

The present disclosure relates to the field of bearing technology, and in particular, to a thrust bearing, a rotor system, and a control method of a thrust bearing.

Background technique

Gas turbines mainly include three major components: compressor, combustion chamber and turbine. After the air enters the compressor, it is compressed into high-temperature and high-pressure air, and then supplied to the combustion chamber to be mixed with the fuel for combustion. The high-temperature and high-pressure gas generated by the compressor expands and works in the turbine. When the rotor rotates at high speed, the rotor is subjected to axial forces. In order to limit the axial movement of the shaft, a thrust bearing needs to be installed in the rotor system. The traditional thrust bearings are ordinary contact bearings. As the rotor speed increases, especially when the rotor speed exceeds 40,000 revolutions per minute, ordinary contact bearings cannot meet the requirements of working speed due to the large mechanical wear. This requires the use of non-contact bearings instead of contact bearings.

In the prior art, non-contact bearings generally include a magnetic bearing and an air bearing. However, magnetic bearings have problems such as high energy consumption and heat generation during long-term opening; while air bearings generate shock waves when the surface linear velocity approaches or exceeds the speed of sound, resulting in bearing instability and even catastrophic consequences such as impact shafts. . It can be seen that the above two non-contact bearings are not suitable for high-speed gas turbine or gas turbine power generation combined units.

It can be seen that there is an urgent need to provide a new control method for thrust bearings, rotor systems and thrust bearings to solve the above problems.

Summary of the invention

The present disclosure provides a control method of a thrust bearing, a rotor system, and a thrust bearing to solve the above problems.

In a first aspect, the present disclosure provides a thrust bearing for mounting on a rotating shaft, the thrust bearing including: a thrust plate fixedly coupled to the rotating shaft; and a threaded on the rotating shaft a first stator and a second stator, the first stator and the second stator are respectively disposed on opposite sides of the thrust disk; the first stator and the second stator, each stator And a magnetic bearing and a foil bearing, wherein the magnetic bearing is provided with a plurality of first magnetic members circumferentially, the foil bearing is provided with a second magnetic member, and the second magnetic member is capable of a magnetic member interacts and generates a magnetic force therebetween; wherein the foil bearing is disposed between the magnetic bearing and the thrust plate, and has a bearing gap with the thrust plate, and the foil The sheet bearing is movable in the axial direction of the rotating shaft by the magnetic force.

Optionally, the magnetic bearing comprises: a magnetic bearing seat, the magnetic bearing seat is disposed opposite to the thrust plate, and a plurality of receiving grooves are arranged on the magnetic bearing seat in a circumferential direction, the plurality of first magnetic bodies a component is disposed in the plurality of receiving slots, and a magnetic pole of the plurality of first magnetic components faces a side where the foil bearing is located; and an end cover disposed at a distance of the magnetic bearing housing One side of the foil bearing is coupled to the foil bearing to secure the first magnetic component to the magnetic bearing housing.

Optionally, the plurality of first magnetic components comprise a plurality of permanent magnets, the plurality of permanent magnets are circumferentially disposed on the magnetic bearing; or the plurality of first magnetic components comprise a plurality of electromagnets The plurality of electromagnets are circumferentially disposed on the magnetic bearing, and each of the plurality of electromagnets includes a magnetic core disposed on the magnetic bearing and wound on the magnetic core Coil.

Optionally, the foil bearing comprises: a foil bearing seat fixedly connected to the magnetic bearing housing; and a first foil and a second foil disposed on the foil bearing housing, the first a foil mounted on the foil bearing housing, the second foil being stacked on a side of the first foil adjacent to the thrust disk; wherein the second foil is a flat foil The second magnetic member is disposed on the second foil such that the second foil can be in the axial direction of the rotating shaft under the magnetic force of the first magnetic member and the second magnetic member Moving in the direction; the first foil is an elastically deformable foil that is elastically deformable when the second foil moves.

Optionally, the first foil is a wave-shaped elastic deformation foil, and the first foil is an unclosed ring having an opening, and one end of the opening is a fixed end, a fixed end fixed to the foil bearing seat, the other end of the opening being a movable end; wherein the second foil is waved on the first foil when the axial direction of the rotating shaft is moved The pattern stretches or contracts, and the movable end moves in the circumferential direction of the ring.

Optionally, the second magnetic component comprises a magnetic material disposed on a side surface of the second foil adjacent to the magnetic bearing; wherein the magnetic material is stripe on the second foil The plurality of strip-shaped magnetic portions are formed in a radial shape or a ring shape; or the magnetic material is distributed in a dot shape on the second foil.

Optionally, the thrust bearing further includes a sensor, the sensor being a combination of any one or more of the following: a displacement sensor for detecting the position of the thrust disc; and detecting a film pressure at the bearing gap a pressure sensor; a speed sensor for detecting the rotational speed of the thrust disk; and an acceleration sensor for detecting the rotational acceleration of the thrust disk.

Optionally, the sensor comprises a sensor cover and a sensor probe, the first end of the sensor probe is connected to the sensor cover, the sensor cover is fixed on the magnetic bearing, the magnetic bearing and the foil bearing a through hole for the sensor probe to pass through; a second end of the sensor probe passes through the magnetic bearing and the through hole in the foil bearing, and extends to the bearing gap, and The second end of the sensor probe is flush with the side of the foil bearing adjacent the thrust pad.

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

In a second aspect, the present disclosure provides a rotor system including a rotating shaft and the thrust bearing of any of the first aspects.

Optionally, the shaft body of the rotating shaft is an integral structure, and the rotating shaft is horizontally disposed or vertically disposed; the rotating shaft is sequentially provided with a motor, a compressor and a turbine; and the rotating shaft is further provided with at least two diameters a bearing, the at least two radial bearings are non-contact bearings; wherein the thrust bearing is disposed at a preset position of the turbine near a side of the compressor, the preset position In order to be able to position the centre of gravity of the rotor system between two of the at least two radial bearings which are furthest apart.

Optionally, the shaft body of the rotating shaft is an integral structure, and the rotating shaft is horizontally disposed or vertically disposed; the rotating shaft is provided with a motor, a compressor, a turbine and two radial bearings, and the two radial bearings are a non-contact bearing; the rotor system further includes a first casing and a second casing, the first casing being coupled to the second casing; wherein the generator, the thrust bearing, and The two radial bearings are disposed in the first casing, the compressor and the through-average are disposed in the second casing, the impeller of the compressor and the turbine impeller Arranged in the second casing.

Optionally, the rotor system is further provided with a locking device for locking the rotating shaft when the rotor system is not working.

Optionally, the locking device comprises a telescopic tightening unit, a connecting rod and a fixing component, one end of the connecting rod is connected to the fixing component, and the other end is connected to the telescopic topping unit, and the telescopic tightening unit is positive The other end of the fixing member is fixedly coupled to the housing on which the rotor system is mounted, to the end face of the rotating shaft away from the end of the turbine.

Optionally, the locking device comprises a telescopic unit and a ferrule, the ferrule is connected to the telescopic end of the telescopic unit, and the ferrule is a semi-circular ferrule having a radius equal to or slightly larger than a radius of the rotating shaft. The axis of the ferrule is disposed in parallel with the axis of the rotating shaft, and the telescopic unit is mounted to a substantially axial intermediate position of the rotating shaft and fixedly coupled to a housing in which the rotor system is mounted.

In a third aspect, the present disclosure provides a method of controlling a thrust bearing, the rotor system according to any one of the second aspect, wherein the plurality of first magnetic components of the thrust bearing are a plurality of electromagnets The method includes: opening a magnetic bearing in the first stator and the second stator, and controlling the thrust disk to move in an axial direction of the rotating shaft under the magnetic force of the plurality of first magnetic members The bearing gap between the thrust disk and the foil bearing in the first stator being equal to the bearing clearance between the thrust disk and the foil bearing in the second stator; After the rotational speed of the rotating shaft is accelerated to the working rotational speed, the magnetic bearings in the first stator and the second stator are closed; when the rotor system is stopped, the first stator and the second stator are turned on a magnetic bearing; after the rotational speed of the rotating shaft is decelerated to zero, the magnetic bearings in the first stator and the second stator are closed.

In a fourth aspect, the present disclosure provides a method of controlling a thrust bearing, the rotor system according to any one of the second aspect, wherein the plurality of first magnetic members of the thrust bearing are a plurality of electromagnets The method includes: opening a magnetic bearing in the first stator and the second stator, and controlling the thrust disk to move in an axial direction of the rotating shaft under the magnetic force of the plurality of first magnetic members The bearing gap between the thrust disk and the foil bearing in the first stator being equal to the bearing clearance between the thrust disk and the foil bearing in the second stator; After the rotation speed of the rotating shaft is accelerated to a first preset value, the magnetic bearings in the first stator and the second stator are closed; when the rotation speed of the rotating shaft is decelerated to a second preset value, the first a magnetic bearing in the stator and the second stator; after the rotational speed of the rotating shaft is decelerated to zero, the magnetic bearings in the first stator and the second stator are closed.

Optionally, the method further includes: when the load is loaded on the thrust plate, the thrust plate moves in an axial direction of the rotating shaft under the load load, the thrust plate and the first set Opening the first stator and the first portion when the bearing gap between the foil bearings in the sub is not equal to the bearing clearance between the thrust disc and the foil bearing in the second stator a magnetic bearing in the two stators; the bearing gap between the thrust disk and the foil bearing in the first stator is equal to between the thrust disk and the foil bearing in the second stator When the bearing gap is closed, the magnetic bearings in the first stator and the second stator are closed.

Optionally, when the load is loaded on the thrust plate, the thrust plate moves in an axial direction of the rotating shaft under the load load, and the thrust disk and the foil bearing in the first stator Opening the magnetic bearing in the first stator and the second stator when the bearing gap between them is not equal to the bearing gap between the thrust disk and the foil bearing in the second stator The method includes: when a load is loaded on the thrust disk, the thrust disk moves in an axial direction of the rotating shaft under a load load, and the thrust disk and the foil bearing in the first stator Controlling the magnetic bearing in the first stator and the second stator when the bearing gap is not equal to the bearing clearance between the thrust disk and the foil bearing in the second stator The maximum power is turned on; or, when the load is loaded on the thrust disk, the thrust disk moves in the axial direction of the rotating shaft under the load load, the thrust disk and the foil in the first stator The bearing clearance between the sheet bearings is not equal to the thrust disc and When the bearing gap between said stator of said second foil bearing, controlling the first stator and the second stator magnetic bearing opening in a stroboscopic manner according to a preset frequency.

In the present disclosure, a gas bearing and a magnetic hybrid thrust bearing are formed by providing a bearing gap and a magnetic bearing in a thrust bearing. In this way, since the gas bearing and the magnetic bearing can work together, the present disclosure can improve the dynamic performance and stability of the thrust bearing, especially in the high-speed operation state, and has strong anti-disturbance capability, thereby improving the bearing capacity of the thrust bearing. It can be seen that the thrust bearing of the present disclosure can meet the requirements of a high-speed gas turbine or a gas turbine power generation combined unit.

DRAWINGS

In order to more clearly illustrate the technical solutions of the embodiments of the present disclosure, the drawings used in the description of the embodiments of the present disclosure will be briefly described below. It is obvious that the drawings in the following description are only some implementations of the present disclosure. For example, other drawings may be obtained from those skilled in the art without any inventive labor.

1 is a schematic structural view of a thrust bearing provided in Embodiment 1;

2 is a schematic structural view of a magnetic bearing in a thrust bearing according to Embodiment 1;

3 is a schematic structural view of a magnetic bearing housing in a thrust bearing according to Embodiment 1;

4 is a schematic structural view of a first foil in a thrust bearing according to Embodiment 1;

FIG. 5 is a schematic structural view of a rotor system according to Embodiment 2; FIG.

6 is a schematic structural view of a rotor system according to Embodiment 3;

7 is a schematic structural view of a rotor system according to Embodiment 4;

8 is a schematic structural view of another rotor system provided in Embodiment 4;

9 is a schematic structural view of a locking device provided in a rotor system according to Embodiment 5;

10 is a schematic structural view of another embodiment of the present invention provided with a locking device in a rotor system;

Figure 11 is a schematic structural view of the C-C direction of Figure 10;

Figure 12 is a schematic view showing the structure of applying an anti-friction coating on a rotating shaft according to Embodiment 6;

13 is a schematic flow chart of a method for controlling a thrust bearing according to Embodiment 7;

14 is a schematic flow chart of another method for controlling a thrust bearing according to Embodiment 7;

Figure 15 is a half cross-sectional view showing a trough type gas-magnetic hybrid radial bearing provided in the eighth embodiment;

Figure 16 is a half cross-sectional view showing another trough type gas-magnetic hybrid radial bearing provided in the eighth embodiment;

Figure 17 is an external view of a trough type gas-magnetic hybrid radial bearing provided in Embodiment 8;

18 is a schematic structural view of a fourth magnetic bearing in a groove type gas-magnetic hybrid radial bearing provided in Embodiment 8;

19 is a schematic structural view of a fourth magnetic bearing housing in a groove type gas magnetic hybrid radial bearing provided in Embodiment 8;

20 is a schematic structural view showing a third dynamic pressure generating groove provided on a second bearing sleeve in a groove type gas magnetic hybrid radial bearing provided in Embodiment 8;

21 is a second structural schematic view showing a third dynamic pressure generating groove disposed on a second bearing sleeve in the groove type gas magnetic hybrid radial bearing provided in the eighth embodiment;

Fig. 22 is a structural schematic view showing a third dynamic pressure generating groove provided on a rotating shaft in the groove type gas-magnetic hybrid radial bearing provided in the eighth embodiment.

Detailed ways

The technical solutions in the embodiments of the present disclosure are clearly and completely described in the following with reference to the accompanying drawings in the embodiments of the present disclosure. It is obvious that the described embodiments are a part of the embodiments of the present disclosure, and not all of the embodiments. All other embodiments obtained by a person of ordinary skill in the art based on the embodiments of the present disclosure without departing from the inventive scope are the scope of the disclosure.

Embodiment 1

As shown in FIG. 1 to FIG. 4, the thrust bearing 500 is mounted on the rotating shaft 100. The thrust bearing 500 includes: a thrust plate 5101, the thrust plate 5101 is fixedly coupled to the rotating shaft 100; and the first portion is disposed on the rotating shaft 100. a stator 5102 and a second stator 5103, the first stator 5102 and the second stator 5103 are respectively disposed on opposite sides of the thrust plate 5101; in the first stator 5102 and the second stator 5103, each stator includes a magnetic bearing 5104 And a foil bearing 5105 having a plurality of first magnetic members circumferentially disposed on the magnetic bearing 5104, the foil bearing 5105 being provided with a second magnetic member capable of generating a magnetic force with the plurality of first magnetic members; wherein the foil The bearing 5105 is disposed between the magnetic bearing 5104 and the thrust plate 5101, and has a bearing gap 5106 with the thrust plate 5101, and the foil bearing 5105 can be driven by the magnetic force between the first magnetic component and the second magnetic component. The 100 moves in the axial direction.

In the embodiment of the present disclosure, the thrust bearing 500 is formed into a gas and magnetic hybrid thrust bearing by providing a bearing gap 5106 and a magnetic bearing 5104 in the thrust bearing 500.

In operation, the gas bearing and the magnetic bearing 5104 in the thrust bearing 500 can work together, relying on the gas bearing to achieve support when the thrust bearing 500 is in a stable working state, and relying on the magnetic force when the thrust bearing 500 is in an unstable working state. The bearing 5104 controls and responds to the thrust bearing 500 in time.

It can be seen that the embodiments of the present disclosure can improve the dynamic performance and stability of the thrust bearing, especially in the high-speed operation state, and have strong anti-disturbance capability, thereby improving the bearing capacity of the thrust bearing. The thrust bearing of the embodiment of the present disclosure can satisfy the requirements of a high-speed gas turbine or gas turbine power generation combined unit and the like.

In the embodiment of the present disclosure, the outer diameters of the thrust disk 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 thrust bearing of the embodiment of the present disclosure is applied to a gas turbine or gas turbine power generation combined unit, the first stator 5102 and the second stator 5103 may be coupled to the casing of the gas turbine through a joint.

Optionally, the plurality of first magnetic components comprise a plurality of permanent magnets, and the plurality of permanent magnets are circumferentially disposed on the magnetic bearing 5104; or the plurality of first magnetic components comprise a plurality of electromagnets, and the plurality of electromagnets are magnetic The bearing 5104 is circumferentially disposed, and each of the plurality of electromagnets includes a magnetic core 51041 disposed on the magnetic bearing 5104 and a coil 51402 wound around the magnetic core.

In the embodiment of the present disclosure, when the thrust bearing 500 only requires the first magnetic component to provide magnetic force without magnetron, the first magnetic component is preferably a permanent magnet; when the thrust bearing 500 simultaneously requires the first magnetic component to provide magnetic force and magnetron, The first magnetic member is preferably an electromagnet.

When the first magnetic member is an electromagnet, a current is supplied to the coil 51402, that is, the magnetic core 51041 can generate a magnetic force. The magnitude of the current flowing into the coil 51402 is different, and the magnitude of the magnetic force generated by the magnetic core 51041 is also different; the direction in which the current is applied to the coil 51402 is different, and the magnetic pole of the magnetic core 51041 is also different.

Among them, since the silicon steel sheet or the silicon steel sheet has physical properties such as high magnetic permeability and low eddy current loss, in a preferred embodiment of the present disclosure, the magnetic core 51041 is formed by laminating a plurality of silicon steel sheets or silicon steel sheets.

Optionally, the magnetic bearing 5104 includes: a magnetic bearing housing 51043. The magnetic bearing housing 51043 is disposed opposite to the thrust plate 5101. The magnetic bearing housing 51043 is circumferentially disposed with a plurality of receiving slots 51044. The plurality of first magnetic components are disposed at a plurality of positions. In the receiving groove 51044, and the magnetic poles of the plurality of first magnetic components face the side where the foil bearing 5105 is located; the end cover 51045, the end cover 51045 is disposed on the side of the magnetic bearing housing 51043 away from the foil bearing 5105, and The foil bearing 5105 is fitted to fix the first magnetic member to the magnetic bearing housing 51043.

Among them, since the silicon steel sheet or the silicon steel sheet has physical properties such as high magnetic permeability and low eddy current loss, in the preferred embodiment of the present disclosure, the magnetic bearing housing 51043 is formed by laminating a plurality of silicon steel sheets or silicon steel sheets. The number of receiving grooves 51044 may be, but not limited to, six or eight, uniformly disposed along the circumferential direction of the magnetic bearing housing 51043. Thus, the magnetic force between the magnetic bearing 5104 and the foil bearing 5105 can be made more uniform and stable. It should be noted that the plurality of first magnetic components may be disposed on the magnetic bearing housing 51043 in other manners, which is not limited thereto. The material of the end cap 51045 may be a non-magnetic material, preferably a hard aluminum material.

Optionally, the foil bearing 5105 includes: a foil bearing housing 51051 fixedly coupled to the magnetic bearing housing 51043; and a first foil 51052 and a second foil 51053 disposed on the foil bearing housing 51051, the first foil The sheet 51052 is mounted on the foil bearing housing 51051, and the second foil 51053 is stacked on the side of the first foil 51052 near the 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 can be in the second The elastically deformable foil which is elastically deformed when the foil 51053 is moved.

The material of the foil bearing housing 51051 is a non-magnetic material, preferably a hard aluminum material. The first foil 51052 is an elastically deformable foil. Considering that the material of the magnetic conductive material is hard and brittle, it is not suitable as an elastic deformation foil. Therefore, the first foil 51052 is preferably a non-magnetic stainless steel belt.

In the embodiment of the present disclosure, by setting the second foil 51053 as a flat foil, it is convenient to control the distance between the second foil 51053 and the thrust plate 5101, or to facilitate controlling the size of the bearing gap 5106; The sheet 51052 adopts an elastically deformable foil, on the one hand, to connect the second foil 51053 and the foil bearing seat 51051, and on the other hand, it can be realized that the second foil 51053 can be along the rotating shaft 100 with respect to the foil bearing housing 51051. The purpose of the axial movement.

Optionally, the first foil 51052 is a wave-shaped elastic deformation foil, and the first foil 51052 is an unclosed ring having an opening, one end of the opening is a fixed end, and the fixed end is fixed to the foil. On the bearing housing 51051, 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 wave pattern on the first foil 51052 is extended or contracted, and the movable end is along the circumference of the ring. Move to.

In the embodiment of the present disclosure, by providing the first foil piece 51052 as a wave-shaped elastic deformation foil, it is convenient to use the stretching or contraction property of the wave pattern to push the second foil piece 51053 to move in the axial direction of the rotary shaft 100. .

It should be noted that the shape of the first foil piece 51052 in the embodiment of the present disclosure is not limited to a wave shape, and other shapes capable of elastic deformation can be applied to the first foil piece 51052 of the embodiment of the present disclosure.

Optionally, the second magnetic component comprises a magnetic material (not shown) disposed on a side surface of the second foil 51053 near the magnetic bearing 5104; wherein the magnetic material is stripped on the second foil 51053 The strips are distributed to form a plurality of strip-shaped magnetic portions, and the plurality of strip-shaped magnetic portions are radially or annular; or the first magnetic members are distributed in a dot shape on the second foil 51053.

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

If the surface of the second foil 51053 completely covers the magnetic material, the magnetic force generated between the magnetic material and the first magnetic member is greatly increased, which easily causes the second foil 51053 to be deformed. In view of this, in the embodiment of the present disclosure, by shielding the surface of the second foil 51053 with a magnetic material, the magnetic material is distributed in a strip shape or a dot shape on the second foil 51053, and the magnetic material can be first The magnetic force generated between the magnetic members is controlled to a reasonable extent, thereby preventing the second foil 51053 from being deformed by an excessive magnetic force.

Optionally, the thrust bearing 500 further includes a sensor 5107, and the sensor probe of the sensor 5107 is disposed in the bearing gap 5106.

In an embodiment of the present disclosure, by providing the sensor 5107, parameters at the bearing gap 5106, such as film pressure at the bearing gap 5106, etc., can be detected in real time. Thus, the magnetic bearing 5104 can actively control the thrust bearing 500 based on the detection result of the sensor 5107, and can achieve high precision in control.

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

In the embodiment of the present disclosure, the sensor 5107 can be more stably disposed on the magnetic bearing 5104 by the configuration and mounting manner of the sensor 5107 described above. In addition, the second end of the sensor probe 51072 is flush with the side of the foil bearing 5105 close to the thrust plate 5101. On the one hand, the sensor probe 51072 can be prevented from being touched by the thrust plate 5101, thereby protecting the sensor probe. 51072; on the other hand, it does not affect the gas film in the bearing gap 5106, and avoids disturbance of the gas film in the bearing gap 5106.

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

In an embodiment of the present disclosure, at least one sensor 5107 should be provided on each stator, preferably a sensor 5107, which is preferably disposed between two adjacent first magnetic members.

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

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

a pressure sensor for detecting a film pressure at a bearing gap 5106;

a speed sensor for detecting the rotational speed of the thrust plate 5101;

An acceleration sensor for detecting the rotational acceleration of the thrust plate 5101.

Embodiment 2

Embodiments of the present disclosure provide a rotor system including: a rotating shaft, the shaft body of the rotating shaft is an integral structure, the rotating shaft is horizontally disposed; a motor, a compressor, and a turbine that are sequentially disposed on the rotating shaft; and, a thrust bearing on the rotating shaft and at least two radial bearings; wherein the thrust bearing is disposed at a preset position of the turbine near a side of the compressor, the preset position being capable of The center of gravity of the rotor system is located between two of the at least two radial bearings that are furthest apart.

In an embodiment of the present disclosure, the thrust bearing is the thrust bearing provided in this application.

In an embodiment of the present disclosure, the thrust bearing is a bearing for restricting movement of the rotating shaft in the axial direction, and the radial bearing is a bearing for restricting movement of the rotating shaft in the radial direction.

With the increase of the rotor speed, ordinary electromagnetic bearings and air bearings can no longer meet the needs of high-speed rotors. Therefore, in the embodiment of the present disclosure, in order to accommodate the development of the high-speed rotation of the rotor, the radial bearing may employ a non-contact bearing.

In the embodiment of the present disclosure, the shaft body of the rotating shaft is an integral structure, and it can be understood that the shaft body of the rotating shaft is a whole shaft, or the shaft body of the rotating shaft is rigidly connected by a plurality of shaft segments. Since the shaft body of the rotating shaft is an integral structure, the strength of the shaft bodies on the rotating shaft is uniform, which makes the position of the thrust bearing on the rotating shaft unrestricted.

Further, in order to maintain the structural stability of the entire rotor system at high speeds, the center of gravity of the entire rotor system should be between the two radial bearings that are furthest apart among the at least two radial bearings. Thus, the entire rotor system forms a spindle structure that differs from conventional cantilever structures, and embodiments of the present disclosure increase the stability of the overall rotor system. Since the position of the thrust bearing at the rotating shaft is not limited, in the embodiment of the present disclosure, the number of the radial bearings of the at least two radial bearings, the position of each radial bearing, and the entire rotor system may be used. The parameters of the mass of each component (including the mass of the thrust bearing itself) are flexibly adjusted to the position of the thrust bearing so that the center of gravity of the entire rotor system is located between the two radial bearings that are furthest apart, preferably The center of gravity of the entire rotor system is located on the compressor.

In the embodiment of the present disclosure, the rotating shaft is horizontally disposed, and therefore, it can be understood that the rotor system of the embodiment of the present disclosure is a horizontal rotor system, which can be applied to a horizontal unit that requires a horizontal rotor system, such as a horizontal gas turbine generator set. .

As shown in FIG. 5, an embodiment of the present disclosure provides a rotor system including a rotating shaft 100 and a thrust bearing 500. The shaft body of the rotating shaft 100 is an integral structure, and the rotating shaft 100 is horizontally disposed. The rotating shaft 100 is sequentially provided with a motor 200 and a compressor. 300 and a turbine 400; a first radial bearing 600 and a second radial bearing 700 are further disposed on the rotating shaft, the first radial bearing 600 and the second radial bearing 700 are both non-contact bearings; the first radial bearing 600 is disposed on 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. 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, when the electromagnetic bearing is opened for a long time, there are problems such as too much energy consumption and heat generation; and when the surface linear velocity approaches or exceeds the speed of sound, a shock wave is generated, which causes the bearing to be unstable and even has catastrophic consequences such as a collision axis. .

Therefore, in consideration of the development demand of the high speed of the gas turbine or the gas turbine generator set, in order to improve the working performance of the radial bearing, in the embodiment of the present disclosure, the first radial bearing 600 may adopt a gas magnetic hybrid radial bearing or a gas dynamic static pressure mixing. Radial bearing. Since the second radial bearing 700 is close to the turbine 400, the second radial bearing 700 may employ a gas dynamic hydrostatic hybrid radial bearing in consideration of the fact that the magnetic member in the magnetic bearing cannot withstand the high temperature transmitted from the turbine 400.

As another embodiment, the second radial bearing 700 may also adopt a pneumatically-mixed radial bearing, in which the magnetic component of the second radial bearing 700 is disposed on the second radial bearing 700 away from the turbine 400. Area. That is, the area on the second radial bearing 700 near the turbine 400 is not provided with a magnetic member.

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

In the embodiment of the present disclosure, 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 the shaft 100 may be provided with a first portion corresponding to the bearing of the motor 200. The dynamic pressure generating groove 201; the motor 200 may also be a heuristic integrated motor, so that when the rotor system is started, the motor 200 can 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 achieve the rotor system to drive the generator to generate electricity.

The thrust bearing 500 and the radial bearing in the rotor system of the embodiment of the present disclosure may also adopt other arrangements, and the embodiments of the present disclosure will not be described one by one because it cannot be exhaustive.

Embodiment 3

An embodiment of the present disclosure provides a rotor system including: a rotating shaft, the shaft body of the rotating shaft is an integral structure, the rotating shaft is vertically disposed; a motor, a compressor, and a turbine that are sequentially disposed on the rotating shaft; a thrust bearing disposed on the rotating shaft and at least two radial bearings; wherein the thrust bearing is disposed at a preset position of the turbine near a side of the compressor, the preset position is The center of gravity of the rotor system can be positioned between two of the at least two radial bearings that are furthest apart.

In the embodiment of the present disclosure, the rotating shaft is vertically disposed, and therefore, it can be understood that the rotor system of the embodiment of the present disclosure is a vertical rotor system, which can be applied to a vertical unit that requires a vertical rotor system, such as a vertical type. Gas turbine generator set.

Since the thrust bearing and the radial bearing are both non-contact bearings, the rotor system can be set upright. In this way, the center of gravity of the rotor system is in the axial center, no static deflection occurs, and the moment generated by gravity on the axis is zero, which can eliminate the influence of gravity on the rotation of the rotor system, thereby improving the stability of the rotor system. At the same time, due to the vertical arrangement of the rotor system, the center of gravity of all components is downward, and the problems caused by the cantilever shaft structure caused by the horizontal arrangement of the rotor system can be avoided.

As shown in FIG. 6 , an embodiment of the present disclosure provides a rotor system including a rotating shaft 100 and a thrust bearing 500. The shaft body of the rotating shaft 100 is an integral structure, and the rotating shaft 100 is vertically disposed; the rotating shaft 100 is sequentially provided with a motor 200 and a gas pressure. The machine 300 and the turbine 400; the first radial bearing 600 and the second radial bearing 700 are further disposed on the rotating shaft, and the first radial bearing 600 and the second radial bearing 700 are both non-contact bearings; The bearing 600 is disposed on 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.

Embodiment 4

An embodiment of the present disclosure provides a rotor system including: a rotating shaft, the shaft body of the rotating shaft is an integral structure, the rotating shaft is horizontally disposed or vertically disposed; a motor, a compressor, a turbine, and a motor disposed on the rotating shaft a thrust bearing and two radial bearings, wherein the two radial bearings are non-contact bearings; and, the first casing and the second casing, the first casing is connected to the second casing; Wherein the motor, the thrust bearing and the two radial bearings are disposed in the first casing, the compressor and the through-average are disposed in the second casing; An impeller of the compressor and the impeller of the turbine are disposed adjacent to each other within the second casing.

With the increase of the rotor speed, the contact bearing has been unable to meet the needs of the high-speed rotor due to the large mechanical wear. Therefore, in the embodiment of the present disclosure, in order to accommodate the development of the high-speed rotation of the rotor, the radial bearing can be a non-contact bearing.

In an embodiment of the present disclosure, the first casing and the second casing may be positioned and connected by a stop (not shown), wherein the thrust bearing and all the radial bearings may all be disposed in the first casing ( It can be understood as the inside of the motor casing, and the second casing (which can be understood as the gas turbine casing) does not need to be provided with bearings. In this way, it is only necessary to ensure the machining precision of the part for setting the bearing stator in the first casing, and the part for connecting the bearing stator in the first casing can be completed by one loading process during assembly. The utility model reduces the processing precision and assembly precision of the gas turbine motor unit, reduces the cost, and is suitable for engineering mass production.

In the embodiment of the present disclosure, the rotating shaft may be disposed horizontally or vertically, and therefore, it is understood that the rotor system of the embodiment of the present disclosure is applicable to both a horizontal unit requiring a rotor system and a rotor to be used. The vertical unit of the system, such as a horizontal gas turbine motor unit, or a vertical gas turbine motor unit.

In the embodiment of the present disclosure, since the shaft body of the rotating shaft is an integral structure, the gas turbine rotor and the motor rotor are connected differently from the prior art by using a coupling. Compared with the prior art, since the shaft body of the rotating shaft is a unitary structure, the strength of the shaft bodies on the rotating shaft is uniform, which makes the position of the thrust bearing on the rotating shaft unrestricted.

In the embodiment of the present disclosure, by arranging the impeller of the compressor against the turbine impeller, the axial length in the first casing is shortened, so that the stability of the entire rotor system can be further improved.

Further, in order to reduce the influence of the heat generated by the turbine on the efficiency of the compressor, a heat insulation layer (not shown) may be disposed on the turbine of the turbine and/or the compressor, wherein the material of the heat insulation layer It can be aerogel or other material with good thermal insulation; turbines of turbines can also be made of materials with lower thermal conductivity, for example turbines made of ceramic materials.

As shown in FIG. 7 , an embodiment of the present disclosure provides a rotor system including a rotating shaft 100 and a thrust bearing 500. The shaft body of the rotating shaft 100 is an integral structure, and the rotating shaft 100 is horizontally disposed. The motor 200 and the compressor are disposed on the rotating shaft 100. 300, a turbine 400, a thrust bearing 500, a first radial bearing 600 and a second radial bearing 700, the first radial bearing 600 and the second radial bearing 700 are both non-contact bearings; and the first casing 800 And the second casing 900, the first casing 800 is 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 on the first casing 800 Inside, the compressor 300 and the turbine 400 are both disposed in the second casing 900.

The first radial bearing 600 is disposed on a side of the motor 200 remote from the second casing 900, the second radial bearing 700 is disposed on a side of the motor 200 adjacent to the second casing 900; and the thrust bearing 500 is disposed at the first diameter Between the 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 demand of the high speed of the gas turbine motor unit, in the embodiment of the present disclosure, the first radial bearing 600 may adopt a pneumatically-mixed radial bearing or a gas dynamic static pressure. The radial bearing is mixed; the second radial bearing 700 may be a pneumatically-mixed radial bearing or a pneumatic hydrostatic 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 disclosure, generally, the weight of the motor 200 and the thrust bearing 500 are both large, and the center of gravity of the entire rotor system is biased toward the side of the first radial bearing 600. In view of this, increasing the bearing capacity of the second radial bearing 700 helps to improve the stability of the entire rotor system.

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

Further, the motor 200 can also be a heuristic integrated motor.

Thus, at the initial start of the rotor system, the motor 200 can be turned on in the start mode to rotate the rotor system. When the speed of the rotor system is raised to the preset speed, the operating mode of the motor 200 can be switched to the power generation mode.

As shown in FIG. 8 , an embodiment of the present disclosure provides another rotor system including a rotating shaft 100 and a thrust bearing 500. The shaft body of the rotating shaft 100 is an integral structure, and the rotating shaft 100 is vertically disposed; the motor 200 disposed on the rotating shaft 100, a compressor 300, a turbine 400, a thrust bearing 500, a first radial bearing 600, and a second radial bearing 700, the first radial bearing 600 and the second radial bearing 700 are both non-contact bearings; and the first machine匣800 and the second casing 900, the first casing 800 is 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 on the first machine In the crucible 800, the compressor 300 and the turbine 400 are both disposed in the second casing 900.

For the rest, reference may be made to the related description in FIG. 7 and the same technical effects can be achieved. To avoid repetition, the embodiments of the present disclosure do not describe this.

Embodiment 5

When the rotor system of the present application is used on a mobile device, such as an extended-range electric vehicle, the rotating shaft is in direct contact with the bearing without the rotor system operating. During the driving process, the rotation of the rotating shaft relative to the radial or axial direction of the bearing due to bumps or vibrations causes wear between the rotating shaft and the bearing, thereby affecting the accuracy and life of the bearing.

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

In the embodiment of the present disclosure, the structure and arrangement of the locking device are not unique. For ease of understanding, two embodiments of the locking system provided with the locking device are specifically described below with reference to FIG. 5.

As shown in FIG. 9 , the locking device 110 includes a telescopic tightening unit 111 , a connecting rod 112 and a fixing component 113 . One end of the connecting rod 112 is connected to the fixing component 113 , and the other end is connected to the telescopic tightening unit 111 . The telescopic tightening unit 111 faces the end surface of the rotating shaft 100 away from the end of the turbine 400, and the other end of the fixing member 113 is fixedly coupled to the housing in which the rotor system of the present application is mounted.

When the rotor system is stopped, the telescopic tightening 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 the thrust plate, thereby axially fixing the rotating shaft 100 while utilizing The friction between the stator of the thrust bearing 500 and the thrust disk radially fixes the rotating shaft 100.

Further, the telescopic tightening unit 111 is provided with a tip portion (not shown), and an end surface of the rotating shaft 100 away from the end of the turbine 400 is provided with a tip hole (not shown). In the locked state, the tip portion is inserted into the top hole of the rotating shaft 100, so that the rotating shaft 100 can be better fixed to prevent wear and damage to the rotating shaft 100 and the bearing during running of the vehicle.

In another embodiment, as shown in FIG. 10 to FIG. 11 , the locking device 120 can also be provided as a locking device of a ferrule structure. Specifically, the locking device 120 includes a telescopic unit 121 and a ferrule 122, and the ferrule 122 is coupled to the telescopic end of the telescopic unit 122. The ferrule 122 may be a semi-circular ferrule having a radius equal to or slightly larger than the radius of the rotating shaft 100. The axis of the ferrule 122 is disposed parallel to the axis of the rotating shaft 100, and the telescopic unit 121 is mounted to a substantially axial intermediate position of the rotating shaft 100, and is fixedly connected. To the housing of the rotor system of the present application.

When the rotor system is stopped, the telescopic unit 121 is extended, so that the ferrule 122 is caught by the rotating shaft 100, and the rotating shaft 100 is pushed into contact with the radial bearing, thereby radially fixing the rotating shaft 100 while utilizing the radial bearing and the rotating shaft 100. The frictional force fixes the shaft 100 axially.

Further, the telescopic unit 121 may select a component such as a piston type cylinder or a hydraulic cylinder that can realize telescopic control.

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

It should be noted that the locking devices of Figs. 9 and 10 are based on the rotor system arrangement shown in Fig. 5, and the locking devices are provided in the rotor system of other embodiments of the present disclosure, which will not be described herein.

In an embodiment of the present disclosure, by providing a locking device, the locking device can lock the shaft when the rotor system is not operating. In this way, it is possible to prevent the rotation of the rotating shaft from being radial or axial with respect to the bearing, so that the accuracy and life of the bearing can be improved.

Embodiment 6

Therefore, in order to solve the above problems, on the basis of other embodiments of the present disclosure, the rotor system of the embodiment of the present disclosure is coated with an anti-friction coating 101 at a portion where the bearing of the rotating shaft 100 is mounted, as shown in FIG.

The wear-resistant coating 101 is applied to the portion of the rotating shaft 100 where the bearing is mounted, and the wear of the rotating shaft 100 and the bearing can be effectively prevented. The wear-resistant coating 101 is preferably a material having chemical stability, corrosion resistance, high lubricating non-stickiness, and good aging resistance, such as polytetrafluoroethylene.

It should be noted that the wear-resistant coating 101 in FIG. 12 is based on the rotor system arrangement shown in FIG. 5, and the locking device is provided in the rotor system of other embodiments of the present disclosure, which will not be described herein.

Example 7

The control method in the rotor system in the thrust bearing of the embodiment of the present disclosure (wherein the first magnetic member in the magnetic bearing is an electromagnet) will be described in detail below.

As shown in FIG. 13 , an embodiment of the present disclosure provides a method for controlling a thrust bearing, including:

S511, opening a magnetic bearing in the first stator and the second stator, and controlling the thrust disk to move in an axial direction of the rotating shaft under the magnetic force of the plurality of magnetic components, so as to make the thrust disk and the foil in the first stator The bearing clearance between the bearings is equal to the bearing clearance between the thrust disk and the foil bearing in the second stator.

Wherein, the specific process of opening the magnetic bearing is: inputting a current signal of a predetermined value to the coil, and the thrust disk reaches a predetermined position between the first stator and the second stator under the action of the magnetic bearing.

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

S513. When the rotor system is stopped, the magnetic bearings in the first stator and the second stator are turned on.

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

In the above process, after the magnetic bearing is opened, the thrust disk reaches the predetermined position between the first stator and the second stator under the action of the magnetic bearing, and the thrust disk has bearing clearances with the end faces of the first stator and the second stator. .

As the shaft rotates, the thrust disk begins to rotate relative to the first and second stators while being lubricated by the airflow in the bearing clearance to prevent wear.

As the rotational speed of the rotating shaft becomes larger and larger, the rotational speed of the thrust disk also increases synchronously. When the rotational speed of the rotating shaft reaches the working rotational speed, the gas dynamic pressure bearing of the thrust bearing (the thrust disk is between the first stator and the second stator) The film pressure generated by setting the bearing clearance, that is, the gas dynamic pressure bearing forming the thrust bearing, can stabilize the thrust plate, and the magnetic bearing can be closed at that time.

When the rotor system is stopped, the thrust plate decelerates as the shaft decelerates. In order to keep the shaft stable during the entire rotor system shutdown, the magnetic bearing is opened when the rotor system is stopped, and the magnetic bearing can be closed after the thrust plate is completely stopped. .

As shown in FIG. 14, an embodiment of the present disclosure further provides another control method of a thrust bearing, including:

S521, opening a magnetic bearing in the first stator and the second stator, and controlling the thrust disk to move in an axial direction of the rotating shaft under the magnetic force of the plurality of magnetic components, so as to make the thrust disk and the foil in the first stator The bearing clearance between the bearings is equal to the bearing clearance between the thrust disk and the foil bearing in the second stator.

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

S523: When the rotation speed of the rotating shaft is decelerated to a second preset value, the magnetic bearings in the first stator and the second stator are turned on.

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

As the rotational speed of the rotating shaft becomes larger and larger, the rotational speed of the thrust disk also increases synchronously. When the rotational speed of the rotating shaft reaches a first preset value, for example, 5% to 30% of the rated rotational speed, the gas dynamic pressure bearing of the thrust bearing ( The film pressure generated by the bearing disc between the thrust disc and the first stator and the second stator, that is, the gas dynamic pressure bearing forming the thrust bearing, can stabilize the thrust disc, and the magnetic bearing can be closed at that time.

During the stop of the rotor system, the thrust plate decelerates as the shaft decelerates. When the speed of the shaft is lower than the second preset value, for example, 5% to 30% of the rated speed, at this time, the gas dynamic pressure bearing of the thrust bearing is generated. The film pressure is also reduced as the thrust plate decelerates. Therefore, the magnetic bearing needs to be opened to keep the thrust plate stable until the thrust plate is completely stopped and the magnetic bearing can be closed.

Optionally, the foregoing method further includes:

When a load is applied to the thrust disk, the thrust disk moves in an axial direction of the rotating shaft under the load load, and the between the thrust disk and the foil bearing in the first stator Opening the magnetic bearing in the first stator and the second stator when the bearing clearance is not equal to the bearing clearance between the thrust disk and the foil bearing in the second stator;

Closing when the bearing gap between the thrust disk and the foil bearing in the first stator is equal to the bearing clearance between the thrust disk and the foil bearing in the second stator a magnetic bearing in the first stator and the second stator.

When the load is loaded on the thrust plate, the bearing clearance between the thrust disk and the foil bearing of the first stator or the second stator is reduced to be close to the foil bearing on the side, the sensor (the sensor here is preferably a pressure sensor) A signal of increased air pressure is obtained, at which point the magnetic bearing needs to be intervened. The magnetic bearing does not directly apply magnetic force to the thrust plate to move it to the foil bearing on the other side, but uses magnetic force to move the foil bearing on the other side away from the thrust disk, so that the thrust disk and the thrust disk The bearing clearance between the foil bearings on the other side is increased, thereby increasing the pressure on the side of the bearing gap, adapting the weight of the load on the thrust plate, and automatically redistributing the airflow pressure on the two bearing gaps. When the thrust plate reaches a new equilibrium position, the magnetic bearing stops working.

Specifically, if the bearing clearance between the thrust disk and the foil bearing in the first stator is smaller than the bearing clearance between the thrust disk and the foil bearing in the second stator, controlling the foil bearing in the second stator is The magnetic force between the plurality of magnetic members and the second magnetic member moves in the axial direction of the rotating shaft in a direction away from the thrust disk.

If the bearing clearance between the thrust disk and the foil bearing in the second stator is smaller than the bearing clearance between the thrust disk and the foil bearing in the first stator, controlling the foil bearing in the first stator in multiple Under the action of the magnetic force between the magnetic member and the second magnetic member, it moves in the axial direction of the rotating shaft in a direction away from the thrust disk.

Optionally, when the load is loaded on the thrust plate, the thrust plate moves in an axial direction of the rotating shaft under the load load, and the thrust disk and the foil bearing in the first stator Opening the magnetic bearing in the first stator and the second stator when the bearing gap between them is not equal to the bearing gap between the thrust disk and the foil bearing in the second stator ,include:

When a load is applied to the thrust disk, the thrust disk moves in an axial direction of the rotating shaft under the load load, and the between the thrust disk and the foil bearing in the first stator Controlling that the magnetic bearing in the first stator and the second stator is turned on at maximum power when the bearing clearance is not equal to the bearing clearance between the thrust disk and the foil bearing in the second stator ;or,

When a load is applied to the thrust disk, the thrust disk moves in an axial direction of the rotating shaft under the load load, and the between the thrust disk and the foil bearing in the first stator Controlling the magnetic bearing in the first stator and the second stator according to a preset frequency when the bearing clearance is not equal to the bearing clearance between the thrust disk and the foil bearing in the second stator Turn on in strobe mode.

When an external impact disturbance occurs, the thrust plate may quickly approach a certain side of the foil bearing, which may cause the bearing clearance on the side to be too small, so that the local gas flow velocity at the side bearing clearance is close to or even reaches the speed of sound, thereby causing The shock wave produces a self-excited air hammer. The generation of shock waves can cause local gas flow to be disturbed and confusing. When the velocity of the fluid changes between sonic and subsonic, its pressure drops stepwise. In this case, the side foil bearing is required to actively "avoid" the thrust disk, thereby increasing the bearing clearance on the side to maintain the air velocity as much as possible in the subsonic range to maintain its normal fluid pressure. Specifically, it is necessary to simultaneously control the magnetic bearings on the first stator and the second stator so that the magnetic poles of the magnetic bearing are excited by the same polarity, that is, the side where the bearing clearance is reduced generates suction for sucking back the side foil The bearing, the side where the bearing clearance is increased, generates suction for pulling back the thrust plate. In this way, the difference in magnetic force between the two sides is used to generate a magnetic difference, thereby pulling the thrust plate to restore the bearing clearance between the thrust plate and the two side foil bearings, thereby bringing the thrust plate back to the equilibrium position.

In the above process, the magnetic bearing is convenient for real-time control, and the unbalanced mass of the thrust plate or the whirl of the thrust plate is actively balanced, which causes the thrust plate to be excessively offset, so that the thrust plate is fixed in the axial direction of the rotating shaft. A very small range. In addition, during the acceleration process of the thrust disk, the position where the shock wave is generated (ie, the linear velocity supersonic portion) can be accurately located, and the magnitude and direction of the current of the magnetic bearing are controlled, so that the magnetic bearing generates an opposite force to balance the shock wave action. . After the shock wave is stable, adjust the control strategy of the magnetic bearing again to fix the thrust plate in a very small range in the most energy-efficient way.

In summary, the preferred embodiment of the present disclosure has the following beneficial effects:

First, the magnetic bearing and the gas bearing work together to improve the dynamic performance and stability of the bearing under high-speed operation, and the resistance to disturbance is strong, thereby improving the bearing capacity of the bearing. At the same time, the magnetic bearing and the gas bearing adopt a parallel structure, which simplifies the structure, has high integration, is easy to process, manufacture and operate, and improves the comprehensive performance of the bearing. When the rotor system is turned on or off, the magnetic bearing can be used to rotate the thrust disc and the stator in the bearing clearance, which improves the low speed performance of the bearing, prolongs the service life of the bearing, and improves the safety and reliability of the bearing and the whole system. Sex.

Second, the thrust bearing of the embodiment of the present disclosure has an advantage of a fast response speed with respect to a conventional gas dynamic hydrostatic hybrid thrust bearing using a combination of a gas static pressure bearing and a gas dynamic pressure bearing.

Thirdly, by providing a magnetic material on the foil, the magnetic pole of the magnetic bearing can appropriately deform the foil, improve the maximum pressure on the lubricating film side of the bearing and prevent leakage of the lubricating gas flow, and improve the thrust plate against the disturbed eccentric collision. The ability of the wall, which in turn increases the bearing capacity of the bearing.

Fourth, the pressure sensor is used to collect the pressure change of the film, and the deformation of the foil is controlled by a simple control method to provide higher rotor damping, thereby improving rotor stability. In addition, due to the simple control method, the machining accuracy of the bearing is not high.

In the present application, the radial bearing in the rotor system can adopt various structural forms. If the radial bearing adopts a pneumatically-mixed radial bearing, it can be a foil-type gas-magnetic hybrid radial bearing or a trough-type pneumatic magnet. Mixed radial bearings.

The specific structural form of the above two radial bearings and the specific control process in the entire rotor system control will be described in detail below with reference to the accompanying drawings.

Example eight

15 to 22 are schematic structural views of a groove type gas magnetic hybrid radial bearing provided by an embodiment of the present disclosure.

As shown in FIG. 15 to FIG. 22, the groove type gas magnetic hybrid radial bearing 6200 includes: a fourth magnetic bearing 6201 sleeved on the rotating shaft 100, and a plurality of seventh magnetic components are circumferentially disposed on the fourth magnetic bearing 6201 The fourth magnetic bearing 6201 is disposed toward the side wall of the rotating shaft 100, or the rotating shaft 100 is disposed on the circumferential surface of the fourth magnetic bearing 6201 with a third dynamic pressure generating groove 6202; wherein the fourth magnetic bearing 6201 and the rotating shaft 100 have the same The four gaps 6203 and the rotating shaft 100 are movable in the radial direction of the rotating shaft 100 by the magnetic force of the plurality of seventh magnetic members.

In the embodiment of the present disclosure, the radial bearing 6200 is formed into a gas-and magnetic-mixed radial bearing by providing a fourth gap 6203 and a fourth magnetic bearing 6201 in the radial bearing 6200.

In operation, the gas bearing in the radial bearing 6200 and the fourth magnetic bearing 6201 can work together, relying on the gas bearing to achieve support when the radial bearing 6200 is in a stable working state; and the radial bearing 6200 is in an unstable operation. In the state, the radial bearing 6200 is controlled and responded in time by the fourth magnetic bearing 6201.

It can be seen that the embodiments of the present disclosure can improve the dynamic performance and stability of the radial bearing, especially in the high-speed operation state, and have strong anti-disturbance capability, thereby improving the bearing capacity of the radial bearing. The radial bearings of the embodiments of the present disclosure are capable of meeting the needs of high speed rotor systems, such as gas turbine or gas turbine power generation combined units.

In the embodiment of the present disclosure, since the silicon steel sheet or the silicon steel sheet has physical properties such as high magnetic permeability and low eddy current loss, the rotating shaft 100 may be formed by laminating a plurality of silicon steel sheets or silicon steel sheets.

In the embodiment of the present disclosure, when the rotating shaft 100 rotates, the flowing gas existing in the fourth gap 6203 is pressed into the third dynamic pressure generating groove 6202, thereby generating pressure to float the rotating shaft 100 to realize the radial direction of the rotating shaft 100. The direction is maintained in a non-contact manner. The magnitude of the pressure generated by the third dynamic pressure generating groove 6202 varies depending on the angle of the third dynamic pressure generating groove 6202, the groove width, the groove length, the groove depth, the number of grooves, and the flatness. Further, the magnitude of the pressure generated by the third dynamic pressure generating groove 6202 is also related to the rotational speed of the rotating shaft 100 and the fourth gap 6203. The parameters of the third dynamic pressure generating groove 6202 can be designed according to actual working conditions. The third dynamic pressure generating groove 6202 may be formed on the fourth magnetic bearing 6201 or the rotating shaft by forging, rolling, etching, or punching.

Optionally, the plurality of seventh magnetic components comprise a plurality of fourth permanent magnets, wherein the plurality of fourth permanent magnets are circumferentially disposed on the fourth magnetic bearing 6201; or the plurality of seventh magnetic components comprise a plurality of fourth electromagnetic components Iron, a plurality of fourth electromagnets are circumferentially disposed on the fourth magnetic bearing 6201, and each of the plurality of fourth electromagnets includes a fourth magnetic core 62011 disposed on the fourth magnetic bearing 6201 and The fourth coil 62012 is wound around the fourth core 62011.

In the embodiment of the present disclosure, when the groove type gas magnetic hybrid radial bearing 6200 only requires the magnetic member to provide magnetic force without magnetron, the seventh magnetic member is preferably a fourth permanent magnet; when the foil type gas magnetic hybrid thrust bearing is simultaneously required In the case of magnetic force and magnetron control, the seventh magnetic member is preferably a fourth electromagnet.

When the seventh magnetic member is the fourth electromagnet, a current is applied to the fourth coil 62012, that is, the fourth magnetic core 62011 can generate a magnetic force. The magnitude of the current flowing into the fourth coil 62012 is different, and the magnitude of the magnetic force generated by the fourth core 62011 is also different. The direction of the current flowing into the fourth coil 62012 is different, and the magnetic poles of the fourth core 62011 are also different.

Wherein, since the silicon steel sheet or the silicon steel sheet has physical properties such as high magnetic permeability and low eddy current loss, in the preferred embodiment of the present disclosure, the fourth magnetic core 62011 may be formed by laminating a plurality of silicon steel sheets or silicon steel sheets.

Optionally, the fourth magnetic bearing 6201 includes: a fourth magnetic bearing housing 62013, the fourth magnetic bearing housing 62013 is sleeved on the rotating shaft 100, and a fourth magnetic receiving seat 62013 is disposed on the fourth magnetic bearing housing 62013 with a plurality of fourth receiving slots 62014 a plurality of seventh magnetic members are disposed in the plurality of fourth receiving grooves 62014, and the magnetic poles of the plurality of seventh magnetic members are oriented toward the rotating shaft 100; and the second bearing housing 62015 is disposed outside the fourth magnetic bearing housing 62013; a second bearing sleeve 62016 between the fourth magnetic bearing housing 62013 and the rotating shaft 100; and a fifth end cover 62017 and a sixth end cover 62018 respectively disposed at two ends of the second bearing housing 62015; wherein, the second bearing sleeve 62016 The fifth end cover 62017 and the sixth end cover 62218 cooperate to fix the plurality of seventh magnetic members to the fourth magnetic bearing housing 62013.

In the embodiment of the present disclosure, by providing the second bearing sleeve 62016, the gap between the fourth core 62011 and the fourth coil 62012 can be closed, thereby forming a stable and uniform gas between the second bearing sleeve 62016 and the rotating shaft 100. Membrane pressure. In addition, the size of the fourth gap 6203 can be conveniently adjusted and controlled by providing the second bearing sleeves 62016 of different radial thicknesses.

The width of the fourth gap 6203 between the second bearing sleeve 62016 and the rotating shaft 100 may be 5 μm to 12 μm, preferably 8 μm to 10 μm.

Wherein, since the silicon steel sheet or the silicon steel sheet has physical properties such as high magnetic permeability and low eddy current loss, in the preferred embodiment of the present disclosure, the fourth magnetic bearing housing 62013 may be formed by laminating a plurality of silicon steel sheets or silicon steel sheets. The number of the fourth accommodating grooves 62014 may be, but not limited to, six or eight, and is uniformly disposed along the circumferential direction of the fourth magnetic bearing housing 62013. Thus, the magnetic force between the fourth magnetic bearing 6201 and the rotating shaft 100 can be made more uniform and stable. It should be noted that the plurality of seventh magnetic members may be disposed on the fourth magnetic bearing housing 62013 in other manners, which is not limited thereto. The material of the fifth end cap 62017 and the sixth end cap 62018 may each be a non-magnetic material, preferably a hard aluminum material. The material of the second bearing sleeve 62016 may be a non-magnetic material, preferably a hard aluminum material. The material of the second bearing shell 62015 may be a non-magnetic material, preferably a hard aluminum material.

Preferably, the fifth end cover 62017 and the sixth end cover 62018 are each provided with a boss having the same outer diameter as the inner diameter of the second bearing shell 62015, and the bosses of the fifth end cover 62017 and the sixth end cover 62218 are used for The end fixes and compacts the silicon steel sheet or the silicon steel sheet constituting the fourth magnetic bearing housing 62013.

In the embodiment of the present disclosure, the third dynamic pressure generating groove 6202 may be disposed on the second bearing sleeve 62016. To facilitate the processing of the third dynamic pressure generating groove 6202, the second bearing sleeve 62016 may be made of a stainless steel material. Specifically, the third dynamic pressure generating groove 6202 may be disposed on the rotating shaft 100 at an intermediate portion corresponding to the circumferential surface of the second bearing sleeve 62016, or may be disposed symmetrically distributed on both sides of the intermediate portion and independent of each other. The pressure generating groove 6202; the third dynamic pressure generating groove 6202 may be disposed at an intermediate portion of the inner side wall of the second bearing sleeve 62016, or may be disposed symmetrically distributed at two ends of the inner side wall of the second bearing sleeve 62016, and independent of each other. The three dynamic pressure generating groove 6202.

Optionally, the third dynamic pressure generating grooves 6202 are arranged in a matrix, so that the gas film is more uniformly distributed in the fourth gap 6203.

Optionally, the third dynamic pressure generating groove 6202 is a continuous or spaced V-shaped groove.

In the embodiment of the present disclosure, by adopting the arrangement of the third dynamic pressure generating groove 6202 described above, the rotating shaft can be held in a non-contact manner in a desired manner in the case where the rotating shaft 100 rotates in the forward direction or the reverse direction. The rotating shaft 100 has the advantages of high load capacity and good stability. The third dynamic pressure generating groove 6202 may be provided as a chevron groove or a groove of other shapes, in addition to being provided as a V-shaped groove.

Optionally, the fourth magnetic bearing 6201 is further provided with a second static pressure air inlet orifice 6205, one end of the second static pressure air inlet orifice 6205 is in communication with the fourth gap 6203, and the other end is connected to an external air source. For conveying an external air source into the fourth gap 6203.

In the embodiment of the present disclosure, the gas static pressure bearing can be formed by providing the second static pressure air intake orifice 6205, so that the groove type gas magnetic hybrid radial bearing 6200 can constitute a trough gas dynamic static pressure-magnetic hybrid diameter. To the bearing. The flow diameter of the second hydrostatic inlet orifice 6205 can be adjusted according to actual working conditions such as gas demand.

Optionally, the second hydrostatic air intake orifice 6205 is divided into at least two branches into the fourth gap 6203 in the fourth magnetic bearing 6201.

In the embodiment of the present disclosure, the second static pressure air intake orifice 6205 may sequentially pass through the fifth end cover 62017 or the sixth end cover 62018, the fourth magnetic bearing 6201, and the second bearing sleeve 62016, and the external air source and The fourth gap 6203 is in communication. Further, the second hydrostatic air intake orifice 6205 can be divided into two or more branches to communicate with the fourth gap 6203 such that the film pressure in the fourth gap 6203 is more uniform. Further, the fifth end cover 62017 or the sixth end cover 62018 may be provided with an annular groove, and a plurality of second static pressure air intake orifices 6205 may be disposed in the annular region corresponding to the fourth magnetic bearing 6201 and the annular groove. For example, a second hydrostatic air intake orifice 6205 is provided in each of the fourth cores 62011 or in every two adjacent fourth cores 62011. The second static pressure inlet orifice 6205 and the flow diameter of the branch can be adjusted according to actual working conditions such as gas demand.

Optionally, the trough type gas magnetic hybrid radial bearing 6200 further includes a plurality of fourth sensors 6204 disposed along a circumferential interval of the fourth magnetic bearing 6201, wherein the sensor probe of each fourth sensor 6204 is disposed in the fourth gap 6203 Inside.

In an embodiment of the present disclosure, by providing the fourth sensor 6204, the parameter at the fourth gap 6203, such as the film pressure at the fourth gap 6203, can be detected in real time. Thus, the fourth magnetic bearing 6201 can actively control the radial bearing 6200 according to the detection result of the fourth sensor 6204, and can achieve high precision in control.

Optionally, each of the plurality of fourth sensors 6204 includes a fourth sensor cover 62041 and a fourth sensor probe 62242. The first end of the fourth sensor probe62042 is connected to the fourth sensor cover 62041, and the fourth sensor The cover 62041 is fixed on the fourth magnetic bearing 6201, and the fourth magnetic bearing 6201 is provided with a through hole for the fourth sensor probe62042 to pass through; the second end of the fourth sensor probe 62242 passes through the fourth magnetic bearing 6201. The through hole extends to the fourth gap 6203, and the second end portion of the fourth sensor probe 62242 is flush with the side of the fourth magnetic bearing 6201 near the rotating shaft 100.

In the embodiment of the present disclosure, the fourth sensor 6204 can be more stably disposed on the fourth magnetic bearing 6201 by the structural form and the mounting manner of the fourth sensor 6204 described above. In addition, the second end portion of the fourth sensor probe 62242 is flush with the side of the fourth magnetic bearing 6201 near the rotating shaft 100. On the one hand, the fourth sensor probe 62242 can be prevented from being touched by the rotating shaft 100, thereby facilitating the contact. The fourth sensor probe 62242 is protected; on the other hand, the air film in the fourth gap 6203 is not affected, and the gas film in the fourth gap 6203 is prevented from being disturbed.

Optionally, each of the plurality of fourth sensors 6204 is disposed between the adjacent two seventh magnetic components.

In an embodiment of the present disclosure, the number of the fourth sensors 6204 may be the same as the number of the seventh magnetic members. The fourth sensor 6204 may be disposed between the two adjacent seventh magnetic components, or may be disposed through the seventh magnetic component, which is not limited by the embodiment of the present disclosure. Each of the fourth sensors 6204 is preferably disposed at a middle portion of the fourth magnetic bearing 6201.

Optionally, the plurality of fourth sensors 6204 are any combination of one or more of the following:

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

a pressure sensor for detecting a film pressure at the fourth gap 6203;

a speed sensor for detecting the rotational speed of the rotating shaft 100;

An acceleration sensor for detecting the rotational acceleration of the rotating shaft 100.

The specific control method when the groove type gas-magnetic hybrid radial bearing of the embodiment of the present disclosure (wherein the seventh magnetic member of the fourth magnetic bearing is an electromagnet) participates in the control process of the rotor system will be described in detail below.

Embodiments of the present disclosure provide a method for controlling a slot type gas magnetic hybrid radial bearing, comprising:

S631, the fourth magnetic bearing is opened, and the rotating shaft is controlled to move in a radial direction of the rotating shaft by a magnetic force of the plurality of seventh magnetic members, and the rotating shaft is pushed to a preset radial position.

S632: After the rotation speed of the rotating shaft is accelerated to the working speed, the fourth magnetic bearing is closed.

S633. When the rotor system is stopped, the fourth magnetic bearing is turned on.

S634: After the rotation speed of the rotating shaft is decelerated to zero, the fourth magnetic bearing is closed.

In the above process, after the fourth magnetic bearing is opened, the rotating shaft is lifted by the fourth magnetic bearing and reaches a preset radial position, and the fourth magnetic bearing and the rotating shaft have a fourth gap.

As the shaft rotates, the shaft begins to rotate under the lubrication of the airflow in the fourth gap to prevent wear. The specific process of opening the fourth magnetic bearing is: inputting a current signal of a predetermined value to the fourth coil, and the rotating shaft is lifted by the fourth magnetic bearing and reaches a preset radial position.

As the rotational speed of the rotating shaft becomes larger and larger, when the rotational speed of the rotating shaft reaches the working rotational speed, the gas dynamic pressure bearing of the radial bearing (the fourth magnetic gap between the fourth magnetic bearing and the rotating shaft forms a gas motion of the radial bearing) The film pressure generated by the pressure bearing can stabilize the shaft, and the fourth magnetic bearing can be closed at that time.

When the rotor system is stopped, the rotating shaft is decelerated. In order to keep the rotating shaft stable during the whole rotor system shutdown, the fourth magnetic bearing is opened when the rotor system is stopped, and the fourth magnetic bearing can be closed after the rotating shaft is completely stopped.

Embodiments of the present disclosure also provide a control method for another trough type gas magnetic hybrid radial bearing, including:

S641, the fourth magnetic bearing is opened, and the rotating shaft is controlled to move in a radial direction of the rotating shaft by a magnetic force of the plurality of seventh magnetic members, and the rotating shaft is pushed to a preset radial position.

S642: After the rotation speed of the rotating shaft is accelerated to a first preset value, the fourth magnetic bearing is closed.

S643. When the rotational speed of the rotating shaft is accelerated to the first critical speed or the second critical speed, the fourth magnetic bearing is turned on.

Specifically, when the gas flow rate at the fourth gap between the rotating shaft and the fourth magnetic bearing reaches a first critical speed or a second critical speed, the fourth magnetic bearing is opened until the rotating shaft returns to the equilibrium radial position.

Optionally, when the rotational speed of the rotating shaft is accelerated to a first-order critical speed or the second-order critical speed, the fourth magnetic bearing is opened, including:

When the rotational speed of the rotating shaft is accelerated to the first critical speed or the second critical speed, the fourth magnetic bearing is controlled to be turned on at the maximum power; or

When the rotational speed of the rotating shaft is accelerated to the first critical speed or the second critical speed, the fourth magnetic bearing is controlled to be turned on in a stroboscopic manner according to a preset frequency.

S644. After the smoothness of the rotor system exceeds the first critical speed or the second critical speed, the fourth magnetic bearing is closed.

S645. During the shutdown of the rotor system, when the rotor system is decelerated to the first critical speed or the second critical speed, the fourth magnetic bearing is turned on.

S646. After the smoothness of the rotor system exceeds the first critical speed or the second critical speed, the fourth magnetic bearing is closed.

S647. When the rotation speed of the rotating shaft is decelerated to the second preset value, the fourth magnetic bearing is turned on.

S648, after the rotation speed of the rotating shaft is decelerated to zero, the fourth magnetic bearing is closed.

As the rotational speed of the rotating shaft becomes larger and larger, when the rotational speed of the rotating shaft reaches a first preset value, for example, 5% to 30% of the rated rotational speed, the radial dynamic bearing of the radial bearing (between the fourth magnetic bearing and the rotating shaft) The film pressure generated by the fourth gap, that is, the gas dynamic pressure bearing forming the radial bearing, can stabilize the shaft, and the fourth magnetic bearing can be closed at that time.

During the stop of the rotor system, the rotating shaft is decelerated. When the rotating shaft speed drops to a second preset value, for example, 5% to 30% of the rated speed, the fourth magnetic bearing is turned on, and the fourth magnetic bearing is turned off until the rotating shaft is completely stopped. Magnetic bearing.

Optionally, the method further includes: when the fourth gap between the rotating shaft and the fourth magnetic bearing changes, opening the fourth magnetic bearing, so that the gap becomes smaller and the corresponding fourth magnetic bearing Moving in a direction close to the rotating shaft by the magnetic force of the plurality of seventh magnetic members;

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

When the load is loaded on the rotating shaft, the rotating shaft is gradually lowered and close to the fourth magnetic bearing below, the fourth sensor (the fourth sensor here is preferably a pressure sensor) obtains a signal of increasing air pressure, and the fourth magnetic bearing needs to be intervened. . The fourth magnetic bearing applies a magnetic force to the rotating shaft to suspend upward, and when the rotating shaft reaches a new equilibrium position, the fourth magnetic bearing stops working.

When an external impact disturbance occurs, the rotating shaft may quickly approach the fourth magnetic bearing, which may cause the gap between the rotating shaft and the fourth magnetic bearing to be too small, so that the local gas flow rate at the reduced gap approaches or even reaches the speed of sound. Therefore, the shock wave is generated by the shock wave. The generation of shock waves can cause local gas flow to be disturbed and confusing. When the velocity of the fluid changes between sonic and subsonic, its pressure drops stepwise. In this case, it is necessary to control the seventh magnetic member of the fourth magnetic bearing to be 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 balanced radial position, the fourth magnetic bearing stops working.

It should be noted that, in the embodiment of the present disclosure, an electromagnetic bearing is provided at the same time (the seventh magnetic component in the fourth magnetic bearing is an electromagnet that forms an electromagnetic bearing) and a hydrostatic bearing (the fourth magnetic bearing is provided). In the case where the second hydrostatic inlet orifice forms a gas hydrostatic bearing, the electromagnetic bearing and the hydrostatic bearing can be used alternately, and in the case where one of the faults, failure or failure to satisfy the opening condition, the other can be used as The spare bearing plays the same role. For example, in the case where an electromagnetic bearing failure is detected, the external air source is turned on to replace the electromagnetic bearing to perform a corresponding action, thereby improving the safety and reliability of the bearing.

In the embodiment of the present disclosure, in the case where the electromagnetic bearing and the hydrostatic bearing are simultaneously provided, for "turning on the hydrostatic bearing in the radial bearing to move the rotating shaft to a predetermined radial position," The steps may include the following implementations:

Opening the fourth magnetic bearing; or, starting an external air source, and conveying the gas to the fourth gap through the second static pressure air intake orifice;

Controlling the rotating shaft to move in a radial direction of the rotating shaft under the action of the magnetic force of the plurality of seventh magnetic members or the pushing of the gas to move the rotating shaft to a predetermined radial position.

In the above process, the fourth magnetic bearing is used to facilitate the advantages of real-time control, and the unbalanced mass of the rotating shaft or the whirl of the rotating shaft is actively balanced, which causes the excessive rotation of the rotating shaft, so that the rotating shaft is fixed in a certain minimum range in the radial direction. Inside. In addition, during the acceleration of the rotating shaft, the position where the shock wave is generated (ie, the linear velocity supersonic portion) can be accurately located, and the fourth magnetic bearing can be balanced by the opposite force by controlling the magnitude and direction of the current of the fourth magnetic bearing. Shock wave action. After the shock wave is stabilized, the control strategy of the fourth magnetic bearing is adjusted again to fix the rotating shaft in a very small range in the most energy-saving manner.

In summary, the embodiments of the present disclosure have the following beneficial effects:

First, the electromagnetic bearing cooperates with the gas bearing to improve the dynamic performance and stability of the bearing under high-speed operation, and has strong resistance to disturbance, thereby improving the bearing capacity of the bearing. At the same time, the electromagnetic bearing and the gas bearing adopt a nested structure, which simplifies the structure, has high integration, is easy to process, manufacture and operate, and improves the comprehensive performance of the bearing. When the rotor system is started or stopped, the bearing can be rotated in the first gap by the electromagnetic bearing, which improves the low-speed performance of the bearing, prolongs the service life of the bearing, and improves the safety of the bearing and the whole system. reliability.

Second, the groove type gas-magnetic hybrid radial bearing of the embodiment of the present disclosure has an advantage of a fast response speed with respect to a conventional gas dynamic static pressure hybrid thrust bearing using a combination of a gas static pressure bearing and a gas dynamic pressure bearing.

Thirdly, the gas hydrostatic bearing is added to form a trough dynamic-static-magnetic hybrid thrust bearing. In the case where electromagnetic bearing and hydrostatic bearing are simultaneously provided, the bearing capacity of the bearing is further increased, and the electromagnetic bearing and the gas static pressure are further increased. The bearings can be used interchangeably, and the other can function as a backup bearing in the event that one of the faults fails, fails, or fails to meet the opening conditions. For example, in the case where an electromagnetic bearing failure is detected, the control system controls the gas hydrostatic bearing to open to replace the electromagnetic bearing to perform a corresponding action, thereby improving the safety and reliability of the bearing.

The above is only the specific embodiment of the present disclosure, but the scope of the present disclosure is not limited thereto, and any person skilled in the art can easily think of changes or substitutions within the technical scope of the disclosure, and should cover It is within the scope of protection of the present disclosure. Therefore, the scope of protection of the disclosure should be determined by the scope of the claims.

Claims

A thrust bearing for mounting on a rotating shaft, characterized in that the thrust bearing comprises:

a thrust plate fixedly coupled to the rotating shaft;

And a first stator and a second stator that are disposed on the rotating shaft, and the first stator and the second stator are respectively disposed on opposite sides of the thrust plate;

Each of the first stator and the second stator includes a magnetic bearing and a foil bearing, and the magnetic bearing is provided with a plurality of first magnetic members circumferentially, and the foil bearing is provided with a first a magnetic member, the second magnetic member being capable of interacting with the plurality of first magnetic members and generating a magnetic force therebetween;

Wherein the foil bearing is disposed between the magnetic bearing and the thrust plate and has a bearing gap with the thrust plate, and the foil bearing can be under the magnetic force on the rotating shaft Move in the axial direction.
The thrust bearing according to claim 1, wherein

The magnetic bearing includes:

a magnetic bearing housing, the magnetic bearing housing is disposed opposite to the thrust disc, the magnetic bearing housing is provided with a plurality of receiving slots in a circumferential direction, and the plurality of first magnetic components are disposed in the plurality of receiving slots And the magnetic poles of the plurality of first magnetic components face the side where the foil bearing is located;

An end cap is disposed on a side of the magnetic bearing housing remote from the foil bearing and cooperates with the foil bearing to fix the first magnetic component to the magnetic bearing housing.
The thrust bearing according to claim 2, characterized in that

The plurality of first magnetic members include a plurality of permanent magnets disposed circumferentially on the magnetic bearing;

Alternatively, the plurality of first magnetic members include a plurality of electromagnets, the plurality of electromagnets are circumferentially disposed on the magnetic bearing, and each of the plurality of electromagnets is disposed on the a magnetic core on the magnetic bearing and a coil wound on the magnetic core.
The thrust bearing according to claim 2, characterized in that

The foil bearing includes:

a foil bearing seat fixedly coupled to the magnetic bearing housing;

And a first foil and a second foil disposed on the foil bearing housing, the first foil is mounted on the foil bearing housing, and the second foil is stacked on the first a side of a foil adjacent to the thrust disk;

Wherein the second foil is a flat foil, and the second magnetic component is disposed on the second foil to enable the second foil to be in the first magnetic component and the second magnetic The magnetic force of the component moves in the axial direction of the rotating shaft; the first foil is an elastically deformable foil capable of being elastically deformed when the second foil moves.
The thrust bearing according to claim 4, characterized in that

The first foil is a wave-shaped elastic deformation foil, and the first foil is an unclosed ring having an opening, one end of the opening is a fixed end, and the fixed end is fixed to The foil bearing housing, the other end of the opening is a movable end;

Wherein, when the second foil moves in the axial direction of the rotating shaft, the wave pattern on the first foil stretches or contracts, and the movable end moves along the circumferential direction of the ring.
The thrust bearing according to claim 4, characterized in that

The second magnetic member includes a magnetic material disposed on a side surface of the second foil adjacent to the magnetic bearing;

Wherein the magnetic material is distributed in a strip shape on the second foil to form a plurality of strip-shaped magnetic portions, the plurality of strip-shaped magnetic portions being radial or annular;

Alternatively, the magnetic material is distributed in dots on the second foil.
The thrust bearing according to claim 1, wherein

The thrust bearing further includes a sensor, which is a combination of any one or more of the following:

a displacement sensor for detecting the position of the thrust disc;

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

a speed sensor for detecting the speed of the thrust disk;

An acceleration sensor for detecting the rotational acceleration of the thrust disk.
The thrust bearing according to claim 7, wherein

The sensor includes a sensor cover and a sensor probe, the first end of the sensor probe is connected to the sensor cover, the sensor cover is fixed on the magnetic bearing, and the magnetic bearing and the foil bearing are provided on the a through hole through which the sensor probe passes; a second end of the sensor probe passes through the through hole of the magnetic bearing and the foil bearing, and extends to the bearing gap, and the sensor probe The second end portion is flush with a side of the foil bearing that is adjacent to the thrust plate.
The thrust bearing according to claim 8, wherein

The sensor is disposed between two adjacent first magnetic members.
A rotor system comprising a rotating shaft and a thrust bearing according to any one of claims 1 to 9.
The rotor system according to claim 10, wherein

The shaft body of the rotating shaft is an integral structure, and the rotating shaft is horizontally disposed or vertically disposed;

a motor, a compressor and a turbine are arranged on the rotating shaft in sequence;

The rotating shaft is further provided with at least two radial bearings, wherein the at least two radial bearings are non-contact bearings;

Wherein the thrust bearing is disposed at a preset position of the turbine near a side of the compressor, the preset position being such that a center of gravity of the rotor system is located at the at least two radial bearings The position between the two radial bearings that are furthest apart.
The rotor system according to claim 10, wherein

The shaft body of the rotating shaft is an integral structure, and the rotating shaft is horizontally disposed or vertically disposed;

The rotating shaft is provided with a motor, a compressor, a turbine and two radial bearings, and the two radial bearings are non-contact bearings;

The rotor system further includes a first casing and a second casing, the first casing being coupled to the second casing;

Wherein the generator, the thrust bearing and the two radial bearings are disposed in the first casing, the compressor and the through-average are disposed in the second casing, The impeller of the compressor is disposed adjacent to the turbine impeller in the second casing.
Rotor system according to claim 11 or 12, characterized in that the rotor system is further provided with a locking device for locking the shaft when the rotor system is not working.
The rotor system according to claim 13, wherein said locking means comprises a telescopic tightening unit, a connecting rod and a fixing member, one end of said connecting rod is connected to said fixing member, and the other end is connected to said telescopic top a tightening unit that faces an end surface of the rotating shaft that is away from the end of the turbine, and the other end of the fixing member is fixedly coupled to a housing on which the rotor system is mounted.
The rotor system according to claim 13, wherein the locking device comprises a telescopic unit and a ferrule, the ferrule is connected to a telescopic end of the telescopic unit, and the ferrule is a semicircular ferrule, The radius is equal to or slightly larger than the radius of the shaft, the axis of the ferrule being disposed parallel to the axis of the shaft, the telescoping unit being mounted to a generally axially intermediate position of the shaft and fixedly coupled to the housing in which the rotor system is mounted.
A method of controlling a thrust bearing for use in a rotor system according to any one of claims 10 to 15, wherein said plurality of first magnetic members of said thrust bearing are a plurality of electromagnets, characterized in that The methods include:

Opening a magnetic bearing in the first stator and the second stator, and controlling the thrust disk to move in an axial direction of the rotating shaft under the magnetic force of the plurality of first magnetic components, so as to The bearing gap between the thrust disk and the foil bearing in the first stator is equal to the bearing clearance between the thrust disk and the foil bearing in the second stator;

After the rotational speed of the rotating shaft is accelerated to the working rotational speed, the magnetic bearings in the first stator and the second stator are closed;

Opening the magnetic bearing in the first stator and the second stator when the rotor system is stopped;

After the rotational speed of the rotating shaft is decelerated to zero, the magnetic bearings in the first stator and the second stator are closed.
A method of controlling a thrust bearing for use in a rotor system according to any one of claims 10 to 15, wherein said plurality of first magnetic members of said thrust bearing are a plurality of electromagnets, characterized in that The methods include:

Opening a magnetic bearing in the first stator and the second stator, and controlling the thrust disk to move in an axial direction of the rotating shaft under the magnetic force of the plurality of first magnetic components, so as to The bearing gap between the thrust disk and the foil bearing in the first stator is equal to the bearing clearance between the thrust disk and the foil bearing in the second stator;

After the rotation speed of the rotating shaft is accelerated to a first preset value, the magnetic bearings in the first stator and the second stator are closed;

When the rotation speed of the rotating shaft is decelerated to a second preset value, the magnetic bearings in the first stator and the second stator are turned on;

After the rotational speed of the rotating shaft is decelerated to zero, the magnetic bearings in the first stator and the second stator are closed.
The method of claim 17, wherein the method further comprises:

When a load is applied to the thrust disk, the thrust disk moves in an axial direction of the rotating shaft under the load load, and the between the thrust disk and the foil bearing in the first stator Opening the magnetic bearing in the first stator and the second stator when the bearing clearance is not equal to the bearing clearance between the thrust disk and the foil bearing in the second stator;

Closing when the bearing gap between the thrust disk and the foil bearing in the first stator is equal to the bearing clearance between the thrust disk and the foil bearing in the second stator a magnetic bearing in the first stator and the second stator.
The method of claim 18, wherein

When a load is applied to the thrust disk, the thrust disk moves in an axial direction of the rotating shaft under the load load, and the between the thrust disk and the foil bearing in the first stator When the bearing clearance is not equal to the bearing clearance between the thrust disk and the foil bearing in the second stator, opening the magnetic bearing in the first stator and the second stator includes:

When a load is applied to the thrust disk, the thrust disk moves in an axial direction of the rotating shaft under the load load, and the between the thrust disk and the foil bearing in the first stator Controlling that the magnetic bearing in the first stator and the second stator is turned on at maximum power when the bearing clearance is not equal to the bearing clearance between the thrust disk and the foil bearing in the second stator ;or,

When a load is applied to the thrust disk, the thrust disk moves in an axial direction of the rotating shaft under the load load, and the between the thrust disk and the foil bearing in the first stator Controlling the magnetic bearing in the first stator and the second stator according to a preset frequency when the bearing clearance is not equal to the bearing clearance between the thrust disk and the foil bearing in the second stator Turn on in strobe mode.