CN208123273U

CN208123273U - A kind of bearing and rotor-support-foundation system

Info

Publication number: CN208123273U
Application number: CN201820053550.3U
Authority: CN
Inventors: 靳普
Original assignee: To Yue Teng Wind Technology Investment Group Ltd
Current assignee: Liu Muhua
Priority date: 2018-01-12
Filing date: 2018-01-12
Publication date: 2018-11-20
Anticipated expiration: 2028-01-12

Abstract

The utility model provides a kind of bearing and rotor-support-foundation system, middle (center) bearing include：Cartridge housing, cartridge housing are hollow revolving body, and cartridge housing is provided with the first accommodating chamber and the second accommodating chamber；The sub- bearing of the radial direction being set in the first accommodating chamber, radial sub- bearing are arranged in shaft, have the first gap between radial sub- bearing and shaft；And the sub- bearing of thrust being set in the second accommodating chamber, the sub- bearing of thrust includes thrust disc, and is respectively arranged at the first stator of thrust disc two sides and the second stator, thrust disc are fixedly connected in shaft, and the first stator and the second stator are arranged in shaft；In first stator and the second stator, there is the second gap between each stator and thrust disc.The utility model is by the way that radial sub- bearing and the sub- bearing of thrust to be integrated in a cartridge housing, its structure is simple, integrated level is high, and it is easily manufactured and installed, it can effectively ensure that the consistent requirement of concentricity of radial sub- bearing and the sub- bearing of thrust in processing and installation.

Description

Bearing and rotor system

Technical Field

The utility model relates to a bearing technical field especially relates to a bearing and rotor system.

Background

The gas turbine mainly comprises three parts of a gas compressor, a combustion chamber and a turbine. After entering the compressor, the air is compressed into high-temperature and high-pressure air, and then the high-temperature and high-pressure air is supplied to the combustion chamber to be mixed and combusted with fuel, and the generated high-temperature and high-pressure gas expands in the turbine to do work. When the rotor rotates at a high speed, the rotor is subjected to a force in a radial direction or an axial direction. In order to limit the radial or axial movement of the rotating shaft, a radial bearing and a thrust bearing are required to be installed in the rotor system. The traditional radial bearing and the thrust bearing are both contact type bearings, and along with the increase of the rotating speed of the rotor, especially when the rotating speed of the rotor exceeds 40000 revolutions per minute, the contact type bearings cannot meet the requirement of the working rotating speed due to the existence of large mechanical abrasion.

In the existing rotor system, a radial bearing and a thrust bearing are processed and installed respectively, so that the requirement that the coaxiality is consistent is difficult to guarantee in the processing or installing process of the radial bearing and the thrust bearing.

SUMMERY OF THE UTILITY MODEL

The utility model provides a bearing and rotor system to solve among the current rotor system and process respectively because of journal bearing and thrust bearing, install and lead to the lower problem of journal bearing and thrust bearing's axiality uniformity.

In a first aspect, the present invention provides a bearing for being installed in a rotating shaft, the bearing includes:

the bearing shell is a hollow revolving body and is provided with a first accommodating cavity and a second accommodating cavity;

the radial sub-bearing is arranged in the first accommodating cavity, the radial sub-bearing is arranged on the rotating shaft in a penetrating mode, and a first gap is formed between the radial sub-bearing and the rotating shaft;

the thrust sub bearing is arranged in the second accommodating cavity and comprises a thrust disc, a first stator and a second stator which are respectively arranged on two sides of the thrust disc, the thrust disc is fixedly connected to the rotating shaft, and the first stator and the second stator are arranged on the rotating shaft in a penetrating mode; each of the first and second stators has a second gap with the thrust disk.

Optionally, the radial sub-bearing includes a first magnetic bearing sleeved on the rotating shaft, the first magnetic bearing and the rotating shaft have a first gap therebetween, and the first magnetic bearing is circumferentially provided with a plurality of first magnetic components; the rotating shaft is movable in a radial direction of the rotating shaft by a magnetic force of the plurality of first magnetic members;

each stator of the first stator and the second stator comprises a second magnetic bearing, and a plurality of second magnetic components are arranged on the second magnetic bearing along the circumferential direction; and a third magnetic component is arranged on the thrust disc, and the thrust disc can move in the axial direction of the rotating shaft under the action of magnetic force between the plurality of second magnetic components and the third magnetic component.

Optionally, the first magnetic bearing comprises:

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

and the bearing sleeve is sleeved between the first magnetic bearing seat and the rotating shaft, the first gap is formed between the bearing sleeve and the rotating shaft, and the bearing sleeve is matched with the first magnetic bearing seat to fix the plurality of first magnetic components on the first magnetic bearing seat.

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

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

Optionally, a first dynamic pressure generating groove is formed in a side wall of the first magnetic bearing facing the rotating shaft or a circumferential surface of the rotating shaft facing the first magnetic bearing.

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

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

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

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

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

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

Optionally, the second magnetic bearing comprises:

the second magnetic bearing seat is opposite to the thrust disc, a plurality of second accommodating grooves are formed in the second magnetic bearing seat along the circumferential direction, the plurality of second magnetic parts are arranged in the plurality of second accommodating grooves, and magnetic poles of the plurality of second magnetic parts face to one side where the thrust disc is located;

the compression ring is arranged on one side, close to the thrust disc, of the second magnetic bearing seat, and the compression ring is matched with the second magnetic bearing seat and fixes the plurality of second magnetic components on the second magnetic bearing seat.

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

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

Optionally, the third magnetic component includes a magnetic material disposed on an end surface of the thrust disk facing the first stator and the second stator;

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

or the magnetic materials are distributed on the thrust disc in a dotted manner.

Optionally, end surfaces of the thrust disk facing the first stator and the second stator, or end surfaces of the first stator and the second stator facing the thrust disk, are provided with a second dynamic pressure generating groove.

Optionally, the second dynamic pressure generating grooves are arranged in a radial or concentric manner.

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

Optionally, a second sensor is further disposed on the thrust sub-bearing, and the second sensor is any one or a combination of more than one of the following sensors:

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

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

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

and the acceleration sensor is used for detecting the rotating acceleration of the thrust disc.

Optionally, the second sensor includes a second sensor cover and a second sensor probe, a first end of the second sensor probe is connected to the second sensor cover, the second sensor cover is fixed to the second magnetic bearing, and a through hole for the second sensor probe to pass through is formed in the second magnetic bearing; the second end of the second sensor probe penetrates through the through hole in the second magnetic bearing and extends to the second gap, and the end part of the second end of the second sensor probe is flush with one side, close to the thrust disc, of the second magnetic bearing.

Optionally, the bearing shell is further provided with a static pressure intake orifice;

one end of the static pressure air inlet throttling hole is connected with an external air source, the other end of the static pressure air inlet throttling hole is communicated with the first gap through the radial sub-bearing and is communicated with the second gap through the first stator and the second stator, and the static pressure air inlet throttling hole is used for conveying the external air source to the first gap and the second gap.

In a second aspect, the present invention provides a rotor system, characterized in that,

the thrust bearing and the at least two radial bearings are non-contact bearings;

the thrust bearing and a radial bearing adjacent to the thrust bearing are integrated to form the bearing of any one of the first aspect.

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

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

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

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

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

the motor, the thrust bearing and the two radial bearings are all arranged in the first casing, the gas compressor and the turbine are arranged in the second casing, and an impeller of the gas compressor and an impeller of the turbine are arranged in the second casing in a leaning mode.

The utility model discloses in, through with radial subbearing and thrust subbearing integration in a bearing housing, its simple structure, integrated level are high, and easily processing and installation, can effectively guarantee the unanimous requirement of the axiality of radial subbearing and thrust subbearing when processing and installation. Additionally, the utility model discloses because all be provided with the clearance in radial subbearing and the thrust subbearing, the utility model discloses a bearing is non-contact bearing, can satisfy the high-speed pivoted demand of rotor.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required to be used in the description of the embodiments of the present invention will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without inventive labor.

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

FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1;

FIG. 3 is a cross-sectional view taken along line B-B of FIG. 1;

FIG. 4 is a schematic structural diagram of a first magnetic bearing seat in a bearing provided in the first embodiment;

FIG. 5 is a schematic structural diagram of a second magnetic bearing seat in the bearing provided in the first embodiment;

fig. 6 is a schematic structural view of a bearing in which a first dynamic pressure generating groove is provided in a bearing housing according to the first embodiment;

fig. 7 is a second schematic structural view of a bearing provided with a first dynamic pressure generating groove in a bearing housing according to the first embodiment;

FIG. 8 is a schematic structural view of a bearing according to the first embodiment, in which a first dynamic pressure generating groove is provided in a rotating shaft;

FIG. 9 is a schematic view showing a structure in which a second dynamic pressure generating groove is provided in a thrust plate in a bearing according to a first embodiment;

FIG. 10 is a second schematic structural view of a bearing according to the first embodiment, in which a second dynamic pressure generating groove is provided in the thrust disk;

fig. 11 is one of schematic structural views of a bearing provided with a second dynamic pressure generating groove provided in a pressure ring according to the first embodiment;

fig. 12 is a second schematic structural view of a bearing according to the first embodiment, in which a second dynamic pressure generating groove is provided in the pressure ring;

FIG. 13 is a schematic structural diagram of a rotor system according to a second embodiment;

FIG. 14 is a schematic structural diagram of a rotor system according to a third embodiment;

FIG. 15 is a schematic structural diagram of a rotor system according to a fourth embodiment;

FIG. 16 is a schematic structural view of another rotor system according to the fourth embodiment;

FIG. 17 is a schematic structural diagram of a locking device provided in a rotor system according to the fifth embodiment;

FIG. 18 is a schematic structural diagram of another locking device provided in a rotor system according to the fifth embodiment;

FIG. 19 is a schematic view of the structure of FIG. 18 in the direction C-C;

FIG. 20 is a schematic view of a sixth embodiment of a wear-resistant coating applied to a rotating shaft;

FIG. 21 is a schematic flowchart illustrating a control method for a bearing according to a seventh embodiment;

FIG. 22 is a schematic flowchart illustrating another bearing control method according to the seventh embodiment;

FIG. 23 is a cross-sectional view of a foil type air-magnetic hybrid radial bearing according to an eighth embodiment;

FIG. 24 is an external view of a foil type air-magnetic hybrid radial bearing provided in accordance with an eighth embodiment;

FIG. 25 is a schematic structural diagram of a third magnetic bearing seat in the foil-type air-magnetic hybrid radial bearing provided in the eighth embodiment;

fig. 26 is a schematic structural diagram illustrating a fourth foil of the foil type air-magnetic hybrid radial bearing according to the eighth embodiment in which a strip-shaped magnetic material is distributed on the fourth foil;

FIG. 27 is a schematic view of the fourth foil shown in FIG. 26 in an expanded configuration;

FIG. 28 is a schematic structural diagram illustrating a fourth foil of the foil-type air-magnetic hybrid radial bearing according to an eighth embodiment having a plurality of point-shaped magnetic materials distributed thereon;

FIG. 29 is a schematic view of the fourth foil shown in FIG. 28 in an expanded configuration;

FIG. 30 is an enlarged schematic view of portion A of FIG. 23;

FIG. 31 is a half sectional view of a groove-type air-magnetic hybrid radial bearing provided in the ninth embodiment;

FIG. 32 is a half sectional view of an alternative groove-type air-magnetic hybrid radial bearing provided in accordance with the ninth embodiment;

FIG. 33 is an outer view of a groove-type air-magnetic hybrid radial bearing provided in accordance with the ninth embodiment;

FIG. 34 is a schematic structural view of a fourth magnetic bearing in the groove-type air-magnetic hybrid radial bearing provided in the ninth embodiment;

FIG. 35 is a schematic structural view of a fourth magnetic bearing seat in the groove-type air-magnetic hybrid radial bearing provided in the ninth embodiment;

fig. 36 is one of schematic structural views showing a third dynamic pressure generating groove provided in the second bearing sleeve in the groove-type air-magnetic hybrid radial bearing provided in the ninth embodiment;

fig. 37 is a second schematic structural view of a groove-type air-magnetic hybrid radial bearing according to the ninth embodiment, in which a third dynamic pressure generating groove is provided in the second bearing sleeve;

fig. 38 is a schematic structural view of a groove-type air-magnetic hybrid radial bearing provided in the ninth embodiment, in which a third dynamic pressure generating groove is provided in the rotating shaft.

Detailed Description

The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, not all, of the embodiments of the present invention. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.

As shown in fig. 1 to 12, a bearing 1000 for being mounted on a rotating shaft 100, the bearing 1000 includes:

a bearing housing 1001, the bearing housing 1001 being a hollow solid of revolution, the bearing housing 1001 being provided with a first accommodation chamber and a second accommodation chamber;

the radial sub-bearing 102 is arranged in the first accommodating cavity, the radial sub-bearing 102 is arranged on the rotating shaft 100 in a penetrating manner, and a first gap 104 is formed between the radial sub-bearing 102 and the rotating shaft 100;

the thrust sub bearing 103 is arranged in the second accommodating cavity, the thrust sub bearing 103 comprises a thrust disc 1031, and a first stator 1032 and a second stator 1033 which are respectively arranged on two sides of the thrust disc 1031, the thrust disc 1031 is fixedly connected to the rotating shaft 100, and the first stator 1032 and the second stator 1033 are both arranged on the rotating shaft 100 in a penetrating manner; in the first stator 1032 and the second stator 1033, each stator has a second gap 105 with the thrust plate 1031.

The embodiment of the utility model provides an in, with integrated in a bearing housing 1001 of radial subbearing 102 and thrust subbearing 103, easily processing and installation have simple structure, the high characteristics of integrated level, can effectively guarantee the unanimous requirement of the axiality of radial subbearing 102 and thrust subbearing 103 when processing and installation. In addition, because be provided with first clearance 104 in the radial sub bearing 102, be provided with second clearance 105 in the thrust sub bearing 103, make the utility model discloses a bearing is non-contact bearing, can satisfy the high-speed pivoted demand of rotor.

Among them, the material of the bearing housing 1001 may be a non-magnetic material, preferably a duralumin material.

The first stator 1032 and the bearing housing 1001 may be integrally formed, and the second stator 1033 and the bearing housing 1001 may be detachably connected.

When the bearing of the embodiment of the present invention is applied to a gas turbine or a gas turbine power generation combined unit, the bearing housing 1001 may be connected to the housing of the gas turbine through a connecting member.

In a preferred embodiment of the present invention, the radial sub-bearing 102 includes a first magnetic bearing 1021 sleeved on the rotating shaft 100, a first gap 104 is provided between the first magnetic bearing 1021 and the rotating shaft 100, and a plurality of first magnetic members 10211 are circumferentially disposed on the first magnetic bearing 1021; the rotation shaft 100 can move in a radial direction of the rotation shaft 100 by a magnetic force of the plurality of first magnetic parts 10211; a first stator 1032 and a second stator 1033, each of which includes a second magnetic bearing 1034, the second magnetic bearing 1034 having a plurality of second magnetic members 10341 arranged in a circumferential direction; the thrust disk 1031 is provided with a third magnetic member, and the thrust disk 1031 is movable in the axial direction of the rotating shaft 100 by a magnetic force between the plurality of second magnetic members 10341 and the third magnetic member.

In the preferred embodiment of the present invention, the radial sub-bearing 102 is formed into a hybrid gas-magnetic radial sub-bearing 102 by providing a first gap 104 and a first magnetic bearing 1021 in the radial sub-bearing 102; the thrust sub-bearing 103 is formed into a hybrid air-magnetic thrust sub-bearing 103 by providing a second gap 105 and a second magnetic bearing 1034 in the thrust sub-bearing 103.

During operation, the radial sub-bearing 102 and the thrust sub-bearing 103 can work cooperatively, so that the rotating shaft 100 is kept stable in both the radial direction and the axial direction; in addition, the gas bearings and the magnetic bearings in the radial sub-bearing 102 and the thrust sub-bearing 103 can also cooperate to control the rotating shaft 100 timely and effectively.

It can be seen that the utility model discloses pivot 100 can be guaranteed to preferred embodiment's bearing, especially dynamic behavior and stability under high-speed running state, and anti disturbance ability is strong, and then has improved the bearing capacity of bearing. The utility model discloses the bearing can satisfy the demand of high rotational speed's gas turbine or gas turbine power generation combined unit etc..

Optionally, the first magnetic bearing 1021 may be detachably mounted within the first receiving cavity.

Further, the bearing further includes an end cap 106, the end cap 106 is disposed at an end portion of the bearing housing 1001 close to the first accommodating cavity, and the end cap 106 abuts against the first magnetic bearing 1021 to fix the first magnetic bearing 1021 in the first accommodating cavity. The material of the end cap 106 may be a non-magnetic material, preferably a duralumin material.

Optionally, the bearing housing 1001 is further provided with a static pressure intake orifice 107; wherein, one end of the static pressure inlet orifice 107 is connected with an external air source, the other end is communicated with the first gap 104 through the radial sub bearing 102 and is communicated with the second gap 105 through the first stator 1032 and the second stator 1033, and the static pressure inlet orifice 107 is used for conveying the external air source to the first gap 104 and the second gap 105.

In the embodiment of the present invention, through setting up the above static pressure air intake orifice 107, thereby making the radial sub-bearing 102 and the thrust sub-bearing 103 all include the aerostatic bearing, thereby the radial sub-bearing 102 can constitute the hybrid radial sub-bearing 102 of gas hybrid dynamic and static pressure-magnetism, and the thrust sub-bearing 103 can constitute the hybrid thrust sub-bearing 103 of gas dynamic and static pressure-magnetism. The flow diameter of the static pressure air inlet orifice 107 can be adjusted according to actual working conditions such as air quantity requirements and the like.

Since the magnetic bearing and the aerostatic bearing are provided at the same time, the bearing capacity of the bearing 1000 can be further increased. In addition, the magnetic bearings and the gas hydrostatic bearings can be mutually standby, and in the case that one of the bearings fails, fails or fails to meet the starting condition, the other bearing can play the same role as a standby bearing. For example, in case of detecting a failure of the magnetic bearing, the safety and reliability of the bearing 1000 are improved by controlling the aerostatic bearing to be opened to perform a corresponding action instead of the magnetic bearing.

For better understanding of the specific structure of each sub-bearing in the bearing according to the embodiment of the present invention, the radial sub-bearing 102 and the thrust sub-bearing 103 are further described below.

Wherein for the radial sub-bearing 102:

as an embodiment, the first magnetic bearing 1021 includes:

the magnetic bearing device comprises a first magnetic bearing seat 10212, wherein the first magnetic bearing seat 10212 is sleeved on the rotating shaft 100, a plurality of first accommodating grooves 10213 are arranged on the first magnetic bearing seat 10212 along the circumferential direction, a plurality of first magnetic parts 10211 are arranged in the plurality of first accommodating grooves 10213, and magnetic poles of the plurality of first magnetic parts 10211 face the rotating shaft 100;

and a bearing housing 10212 sleeved between the first magnetic bearing holder 10212 and the rotating shaft 100, wherein a first gap 104 is formed between the bearing housing 10212 and the rotating shaft 100, and the bearing housing 10212 is matched with the first magnetic bearing holder 10212 to fix the plurality of first magnetic components 10211 on the first magnetic bearing holder 10212.

In this embodiment, by providing the bearing housing 10212, the gap between the magnetic core 1011 and the coil 1012 and the first magnetic bearing holder 10212 can be closed, and a stable and uniform air film pressure can be formed between the bearing housing 10212 and the rotating shaft 100. In addition, the size of the first gap 104 can be easily adjusted and controlled by providing the bearing housing 10212 with different radial thicknesses.

Wherein, a width of the first gap 104 between the bearing housing 10212 and the rotation shaft 100 may be 5 μm to 12 μm, preferably 8 μm to 10 μm.

It should be noted that, when the rotating shaft 100 is not opened, the rotating shaft 100 and the bearing sleeve 10212 are coaxially disposed, and after the rotating shaft 100 is opened, the axis of the rotating shaft 100 deviates from any side of the axis of the bearing sleeve 10212, and the eccentricity epsilon is 0.3 to 0.5, so as to ensure that a wedge-shaped first gap 104 can be formed between the bearing sleeve 10212 and the rotating shaft 100. As the shaft 100 rotates, gas is forced into the first gap 104, thereby creating pressure to support the load. Where, the eccentricity e/(R-R) is the distance between the axis of the rotating shaft 100 and the axis of the bearing sleeve 10212, R is the inner diameter of the rotating shaft 100, and (R-R) is the width of the bearing gap.

Wherein, because silicon steel sheet or silicon steel sheet have physical characteristics such as magnetic permeability is high, eddy current loss is low, the utility model discloses a preferred embodiment, first magnetic bearing seat 10212 is laminated by a plurality of silicon steel sheets or silicon steel sheet and is formed. The number of the first receiving grooves 10213 may be, but is not limited to, six or eight, and are uniformly arranged along the circumferential direction of the first magnetic bearing holder 10212. In this way, the magnetic force of the first magnetic bearing 1021 can be made more uniform and stable. The plurality of first magnetic units 10211 may be disposed on the first magnetic bearing base 10212 in other manners, which are not limited. The material of the bearing housing 10212 may be a non-magnetic material, preferably a duralumin material.

As an embodiment, the plurality of first magnetic components 10211 includes a plurality of first permanent magnets circumferentially disposed on the first magnetic bearing 1021; alternatively, the plurality of first magnetic components 10211 include a plurality of first electromagnets disposed circumferentially on the first magnetic bearing 1021, and each of the plurality of first electromagnets includes a first magnetic core disposed on the first magnetic bearing 1021 and a first coil wound on the first magnetic core.

In this embodiment, when the radial sub-bearing 102 only requires the first magnetic part 10211 to provide magnetic force without magnetic control, the first magnetic part 10211 is preferably a permanent magnet; when the radial sub-bearing 102 requires both the magnetic force and the magnetic control of the first magnetic member 10211, the first magnetic member 10211 is preferably an electromagnet.

When the first magnetic component 10211 is an electromagnet, a current is applied to the first coil to generate a magnetic force in the first magnetic core. The magnitude of the current led into the first coil is different, and the magnitude of the magnetic force generated by the first magnetic core is also different; the direction of current passing to the first coil is different, and the magnetic poles of the first magnetic core are also different.

Wherein, because silicon steel sheet or silicon steel sheet have physical properties such as magnetic permeability height, eddy current loss low, the utility model discloses a preferred embodiment, first magnetic core can be laminated by a plurality of silicon steel sheets or silicon steel sheet and form.

In one embodiment, a sidewall of the first magnetic bearing 1021 facing the rotating shaft 100 and/or a circumferential surface of the rotating shaft 100 facing the first magnetic bearing 1021 is provided with a first dynamic pressure generating groove 1022.

In this embodiment, when the rotating shaft 100 rotates, the flowing gas existing in the first gap 104 is pressed into the first dynamic pressure generating groove 1022, thereby generating a pressure to float the rotating shaft 100 upward, so that the rotating shaft 100 is held in a non-contact manner in the radial direction. The pressure generated by the first dynamic pressure generating grooves 1022 varies with the angle, groove width, groove length, groove depth, number of grooves, and flatness of the first dynamic pressure generating grooves 1022. The magnitude of the pressure generated by the first dynamic pressure generating groove 1022 is also related to the rotational speed of the rotating shaft 100 and the first gap 104. The parameters of the first dynamic pressure generating groove 1022 may be designed according to actual conditions. The first dynamic pressure generating grooves 1022 may be formed on the first magnetic bearing 1021 or the rotating shaft 100 by forging, rolling, etching, or punching.

In this embodiment, in combination with the previous embodiment, the first dynamic pressure generating grooves 1022 may be provided on the bearing housing 10212, and the bearing housing 10212 may be made of a stainless steel material in order to facilitate the machining of the first dynamic pressure generating grooves 1022. Specifically, the first dynamic pressure generating grooves 1022 may be disposed at a middle portion of the rotating shaft 100 corresponding to the circumferential surface of the bearing housing 10212, or may be disposed at two independent first dynamic pressure generating grooves 1022 symmetrically disposed at two sides of the middle portion; the first dynamic pressure generating grooves 1022 may be formed in the middle of the inner sidewall of the bearing housing 10212, or may be formed in two independent first dynamic pressure generating grooves 1022 symmetrically distributed at both ends of the inner sidewall of the bearing housing 10212.

Alternatively, the first dynamic pressure generating grooves 1022 are arranged in a matrix. This is advantageous in that the gas film is more evenly distributed in the first gap 104.

Further, the first dynamic pressure generating grooves 1022 are V-shaped grooves provided continuously or at intervals. Thus, the rotating shaft 100 can be contactlessly held in a desired manner in the case where the rotating shaft 100 is rotated in the forward direction or in the reverse direction, so that the rotating shaft 100 has advantages of high load capacity and good stability. The first dynamic pressure generating grooves 1022 may be provided as chevron-shaped grooves or grooves of other shapes, in addition to the V-shaped grooves.

As an embodiment, the radial sub-bearing 102 further includes a plurality of first sensors (not shown) disposed at intervals along a circumference of the first magnetic bearing 1021, wherein a sensor probe of each first sensor is disposed within the first gap 104.

In this way, parameters at the first gap 104, such as the air film pressure at the first gap 104, etc., can be detected in real time. In this way, the first magnetic bearing 1021 can actively control the radial sub-bearing 102 according to the detection result of the first sensor, and can achieve a high degree of control accuracy.

Optionally, each of the plurality of first sensors includes a first sensor cover and a first sensor probe, a first end of the first sensor probe is connected to the first sensor cover, the first sensor cover is fixed to the first magnetic bearing 1021, and the first magnetic bearing 1021 is provided with a through hole for the first sensor probe to pass through; the second end of the first sensor probe passes through the through hole of the first magnetic bearing 1021 and extends to the first gap 104, and the second end of the first sensor probe is flush with the side of the first magnetic bearing 1021 that is close to the rotating shaft 100.

In this way, the first sensor can be more stably provided on the first magnetic bearing 1021. In addition, the second end of the sensor probe is flush with the first magnetic bearing 1021 on the side close to the rotating shaft 100, so that the sensor probe can be prevented from being touched by the rotating shaft 100, and the protection of the sensor probe is facilitated.

Optionally, each of the plurality of first sensors is disposed between two adjacent first magnetic components 10211. For example, when the number of the first magnetic parts 10211 is eight, the number of the first sensors may also be eight, each first sensor is respectively disposed between two adjacent first magnetic parts 10211, and each first sensor is preferably disposed in the middle of the first magnetic bearing 1021.

Optionally, the plurality of first sensors are any one or a combination of more than one of the following:

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

a pressure sensor for detecting the pressure of the air film at the first gap 104;

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

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

Wherein, for the thrust sub-bearing 103:

as an embodiment, the second magnetic bearing 1034 includes:

a second magnetic bearing seat 10342, where the second magnetic bearing seat 10342 is disposed opposite to the thrust disk 1031, a plurality of second receiving grooves 10343 are circumferentially disposed on the second magnetic bearing seat 10342, the plurality of second magnetic members 10341 are disposed in the plurality of second receiving grooves 10343, and magnetic poles of the plurality of second magnetic members 10341 face a side where the thrust disk 1031 is located;

the pressure ring 10344 is provided on the second magnetic bearing holder 10342 on a side close to the thrust plate 1031, and the pressure ring 10344 is fitted to the second magnetic bearing holder 10342 to fix the plurality of second magnetic members 10341 to the second magnetic bearing holder 10342.

Wherein, because the silicon steel sheet or the silicon steel sheet have physical properties such as high magnetic permeability, low eddy current loss, etc., in the preferred embodiment of the present invention, the second magnetic bearing seat 10342 is formed by laminating a plurality of silicon steel sheets or silicon steel sheets. The number of the second receiving grooves 10343 may be, but not limited to, six or eight, and is uniformly arranged along the circumferential direction of the second magnetic bearing holder 10342. In this way, the magnetic force between the second magnetic bearing 1034 and the thrust disk 1031 can be made more uniform and stable. The plurality of second magnetic members 10341 may be provided on the second magnetic bearing holder 10342 in another manner, which is not limited to this. The material of the pressure ring 10344 may be a non-magnetic material, preferably a duralumin material.

In accordance with the structure of the embodiment, the air intake path of the static pressure air intake orifice 107 is communicated with the annular gas flow passage of the first stator 1032 and the annular gas flow passage of the second stator 1033 in two ways in the bearing housing 1001, one end of the static pressure air intake path of the first stator 1032 and the second stator 1033 is communicated with the second gap 105 between the thrust plate 1031 and the two stators by passing through the pressure ring 10344, and the other end is communicated with the annular gas flow passage of the first stator 1032 and the annular gas flow passage of the second stator 1033.

As an embodiment, the plurality of second magnetic parts 10341 includes a plurality of second permanent magnets circumferentially disposed on the second magnetic bearing 1034;

alternatively, the plurality of second magnetic members 10341 includes a plurality of second electromagnets that are circumferentially disposed on the second magnetic bearing 1034, and each of the plurality of second electromagnets includes a second magnetic core that is disposed on the second magnetic bearing 1034 and a second coil that is wound around the second magnetic core.

In the embodiment of the present invention, when the sub-thrust bearing 103 only needs the second magnetic member 10341 to provide magnetic force and does not need magnetic control, the second magnetic member 10341 is preferably a permanent magnet; when the thrust sub-bearing 103 requires the second magnetic member 10341 to provide both magnetic force and magnetic control, the second magnetic member 10341 is preferably an electromagnet.

When the second magnetic member 10341 is an electromagnet, a current is applied to the second coil, so that the second magnetic core generates a magnetic force. The magnitude of the current led into the second coil is different, and the magnitude of the magnetic force generated by the second magnetic core is also different; the direction of current passing through the second coil is different, and the magnetic poles of the second magnetic core are also different.

Wherein, because silicon steel sheet or silicon steel sheet have physical properties such as magnetic permeability height, eddy current loss low, the utility model discloses a preferred embodiment, the second magnetic core is folded by a plurality of silicon steel sheets or silicon steel sheet and is pressed and form.

As an embodiment, the third magnetic component includes a magnetic material (not shown in the figure) disposed on an end surface of the thrust disk 1031 facing the first stator 1032 and the second stator 1033;

wherein, the magnetic material is distributed on the thrust disc 1031 in a strip shape to form a plurality of strip-shaped magnetic portions, and the plurality of strip-shaped magnetic portions are radial or annular;

alternatively, the magnetic material is distributed in a dot shape on the thrust plate 1031.

In this embodiment, the magnetic material is distributed in a stripe shape or a dot shape on the thrust plate 1031, and the magnetic force generated between the magnetic material and the second magnetic member 10341 can be controlled within a reasonable range.

In one embodiment, the thrust disk 1031 has an end surface facing the first stator 1032 and the second stator 1033, and/or the first stator 1032 and the second stator 1033 have a second dynamic pressure generating groove 1035 formed on an end surface facing the thrust disk 1031.

In the embodiment of the present invention, when the thrust disk 1031 rotates, the flowing gas existing in the second gap 105 is pressed into the second dynamic pressure generating groove 1035, thereby generating pressure to realize that the thrust disk 1031 is held in a non-contact manner in the axial direction. The pressure generated by the second dynamic pressure generating grooves 1035 varies with the angle, groove width, groove length, groove depth, number of grooves, and flatness of the second dynamic pressure generating grooves 1035. The magnitude of the pressure generated by the second dynamic pressure generating groove 1035 is also related to the rotational speed of the thrust disk 1031 and the second gap 105. The parameters of the second dynamic pressure generating groove 1035 may be designed according to actual conditions. The second dynamic pressure generating grooves 1035 may be formed on the first stator 1032 and the second stator 1033 by forging, rolling, etching, or punching, or the second dynamic pressure generating grooves 1035 may be formed on the thrust plate 1031 by forging, rolling, etching, or punching.

In this embodiment, in combination with the foregoing embodiment, the second dynamic pressure generating grooves 1035 may be provided on the pressure ring 10344, and the pressure ring 10344 may be made of a stainless steel material in order to facilitate the machining of the second dynamic pressure generating grooves 1035.

Alternatively, the second dynamic pressure generating grooves 1035 may be arranged in a radial or concentric manner. This is advantageous in that the gas film is more evenly distributed in the second gap 105.

Alternatively, the second dynamic pressure generating groove 1035 includes a first spiral groove 10351 and a second spiral groove 10352, the first spiral groove 10351 surrounds the second spiral groove 10352, the spiral direction of the first spiral groove 10351 is opposite to that of the second spiral groove 10352, and one end of the first spiral groove 10351 adjacent to the second spiral groove 10352 is connected to or disconnected from one end of the second spiral groove 10352 adjacent to the first spiral groove 10351.

The distance from the end of the first spiral groove 10351 close to the second spiral groove 10352 to the axial center of the rotating shaft 100 is equal to the distance from the end of the first spiral groove 10351 close to the second spiral groove 10352 to the outer peripheral edge of the first stator 1032, the second stator 1033, or the thrust plate 1031. Alternatively, the distance from the end of the second spiral groove 10352 close to the first spiral groove 10351 to the axial center of the rotating shaft 100 is equal to the distance from the end of the second spiral groove 10352 close to the first spiral groove 10351 to the outer peripheral edge of the first stator 1032, the second stator 1033, or the thrust plate 1031.

Thus, the thrust plate 1031 can be held in a desired manner in a non-contact manner in the case where the rotation shaft 100 is rotated in the forward direction or the reverse direction, so that the rotation shaft 100 has advantages of high load capacity and good stability.

In one embodiment, the thrust sub-bearing 103 is further provided with a second sensor (not shown), and a sensor probe of the second sensor is disposed in the second gap 105.

In this way, a parameter at the second gap 105, such as the gas film pressure at the second gap 105, etc., can be detected in real time. In this way, the second magnetic bearing 1034 can actively control the thrust sub-bearing 103 based on the detection result of the second sensor, and can achieve high accuracy of control.

Optionally, the second sensor includes a second sensor cover and a second sensor probe, a first end of the second sensor probe is connected to the second sensor cover, the second sensor cover is fixed on the second magnetic bearing 1034, and a through hole for the second sensor probe to pass through is formed in the second magnetic bearing 1034; the second end of the second sensor probe passes through the through hole in the second magnetic bearing 1034 and extends to the second gap 105, and the second end of the second sensor probe is flush with the side of the second magnetic bearing 1034 close to the thrust disc 1031.

In this way, the second sensor can be more stably mounted on the second magnetic bearing 1034. In addition, the second end of the second sensor probe is flush with the side of the second magnetic bearing 1034 close to the thrust disc 1031, so that the second sensor probe can be prevented from being touched by the thrust disc 1031, and the protection of the second sensor probe is facilitated.

Alternatively, the second sensor is disposed between two adjacent second magnetic members 10341.

At least one second sensor, preferably one second sensor, is provided on each stator, which second sensor is preferably arranged between two adjacent second magnetic components 10341.

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

a displacement sensor for detecting the position of the thrust plate 1031;

a pressure sensor for detecting a pressure of the air film at the second gap 105;

a speed sensor for detecting a rotational speed of the thrust plate 1031;

an acceleration sensor for detecting the rotational acceleration of the thrust plate 1031.

Example two

An embodiment of the utility model provides a rotor system, include:

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

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

the thrust bearing and the at least two radial bearings are arranged on the rotating shaft, and the thrust bearing and the at least two radial bearings are non-contact bearings;

In the embodiment of the utility model provides an in, thrust bearing and with the adjacent radial bearing of thrust bearing is integrated integrative, forms the bearing that provides in this application.

The embodiment of the utility model provides an in, thrust bearing is for being used for restricting the bearing that the pivot removed in the axial direction, and radial bearing is for being used for restricting the bearing that the pivot removed in the radial direction.

With the increase of the rotating speed of the rotor, the common bearings can not meet the requirement of the high-rotating-speed rotor. Therefore, in the embodiment of the present invention, in order to adapt to the development demand of the high-speed rotation of the rotor, the thrust bearing and the radial bearing can both adopt non-contact bearings.

The embodiment of the utility model provides an in, the axis body structure as an organic whole of pivot can be understood, and the axis body of pivot is a whole axle, and perhaps, the axis body of pivot forms through a plurality of shaft sections rigid connection. Because the axis body of pivot is structure as an organic whole, the intensity of the axis body everywhere in the pivot has the uniformity, and this makes thrust bearing be unrestricted in the epaxial position that sets up of pivot.

Further, in order to keep the entire rotor system stable in structure even when rotating at a high speed, the center of gravity of the entire rotor system should be located between the two radial bearings which are farthest away from each other among the at least two radial bearings. Like this, whole rotor system forms the spindle structure, is different from traditional cantilever type structure, the embodiment of the utility model provides an improved whole rotor system's stability. Because thrust bearing is unrestricted at the position that sets up of pivot, consequently, the embodiment of the utility model provides an in, can be according to above-mentioned two at least radial bearing's the quantity that sets up, every radial bearing set up the position and the whole rotor system in the quality (including thrust bearing self quality) isoparametric of each part to thrust bearing's the position that sets up adjust in a flexible way to make whole rotor system's focus be located between two radial bearing at a distance from the farthest, preferred, whole rotor system's focus is located the compressor.

The embodiment of the utility model provides an in, the pivot level sets up, consequently, can understand ground, the utility model discloses the rotor system is horizontal rotor system, and it can be applicable to the horizontal unit that needs use horizontal rotor system, for example horizontal gas turbine generating set.

As shown in fig. 13, an embodiment of the present invention provides a rotor system, which includes a rotating shaft 100 and a thrust bearing 500, wherein a shaft body of the rotating shaft 100 is an integral structure, and the rotating shaft 100 is horizontally disposed;

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

the rotating shaft is further provided with a first radial bearing 600 and a second radial bearing 700, the first radial bearing 600 and the second radial bearing 700 are non-contact bearings, wherein the first radial bearing 600 and the thrust bearing 500 are integrated into a whole to form an integrated bearing 10000;

the first radial bearing 600 is disposed on a side of the motor 200 away 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.

At present, the non-contact bearing generally includes an electromagnetic bearing and an air bearing. However, the electromagnetic bearing has the problems of too large energy consumption, heat generation and the like when being started for a long time; when the surface linear velocity of the air bearing is close to or exceeds the sonic velocity, shock waves can be generated, so that the bearing is unstable, and even disastrous results such as shaft collision and the like are generated.

Therefore, consider the development demand of gas turbine or the high rotational speed of gas turbine generating set, in order to improve journal bearing's working property, the embodiment of the utility model provides an in, first journal bearing 600 can adopt the mixed journal bearing of gas magnetism or gaseous hybrid journal bearing of sound and static pressure. The second radial bearing 700 is close to the turbine 400, and the second radial bearing 700 may employ a hybrid gas hybrid radial bearing in consideration of the magnetic components in the magnetic bearings that cannot withstand the high temperature from the turbine 400.

In another embodiment, the second radial bearing 700 may also be a hybrid gas-magnetic radial bearing, in which case the magnetic components of the second radial bearing 700 are arranged on the second radial bearing 700 in a region remote from the turbine 400. That is, the second radial bearing 700 is not provided with magnetic components in the region close to the turbine 400.

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

In the embodiment of the present invention, the compressor 300 may be a centrifugal compressor 300, and the turbine 400 may be a centrifugal turbine; the motor 200 may be a dynamic pressure bearing motor, and a first dynamic pressure generating groove 201 may be disposed at a portion of the rotating shaft 100 corresponding to a bearing of the motor 200; the motor 200 may also be a starting integrated motor, so that when the rotor system is started, the motor 200 may be used as a motor to drive the rotor system to rotate; after the rotor system is started, the motor 200 can be used as a generator to generate electricity by driving the generator with the rotor system.

The utility model discloses thrust bearing and journal bearing among the rotor system of embodiment can also adopt other modes of setting, because unable exhaustively, the embodiment of the utility model provides a no longer explain one by one.

EXAMPLE III

An embodiment of the utility model provides a rotor system, include:

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

With the increase of the rotating speed of the rotor, the common bearings can not meet the requirement of the high-rotating-speed rotor. Therefore, in the embodiment of the present invention, in order to adapt to the development demand of the high-speed rotation of the rotor, the radial bearing may adopt a non-contact bearing.

The embodiment of the utility model provides an in, the vertical setting of pivot, consequently, can understand, the utility model discloses rotor system is vertical rotor system, and it can be applicable to the vertical unit that needs use vertical rotor system, for example vertical gas turbine generating set.

Because the thrust bearing and the radial bearing both adopt non-contact bearings, the rotor system can be vertically arranged. Therefore, the gravity center of the rotor system is positioned at the axis, static deflection cannot be generated, the moment generated on the axis by the gravity is zero, the influence of the gravity on the rotation of the rotor system can be eliminated, and the stability of the rotor system can be improved. Meanwhile, the rotor system is arranged vertically, the gravity centers of all the components are downward, and the problem caused by a cantilever shaft type structure due to the horizontal arrangement of the rotor system can be avoided.

As shown in fig. 14, an embodiment of the present invention provides a rotor system, which includes a rotating shaft 100 and a thrust bearing 500, wherein a shaft body of the rotating shaft 100 is an integral structure, and the rotating shaft 100 is vertically disposed;

Example four

An embodiment of the utility model provides a rotor system, include:

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

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

the first casing is connected with the second casing;

the motor, the thrust bearing and the two radial bearings are all arranged in the first casing, and the gas compressor and the turbine are arranged in the second casing; and the impeller of the compressor and the impeller of the turbine are arranged in the second casing in a leaning way.

With the increase of the rotating speed of the rotor, the contact type bearing can not meet the requirement of the high-rotating-speed rotor due to the existence of large mechanical abrasion. Therefore, in the embodiment of the present invention, in order to adapt to the development requirement of the high-speed rotation of the rotor, the radial bearing may adopt a non-contact bearing.

In an embodiment of the present invention, the first casing and the second casing can be positioned and connected through a spigot (not shown in the figure), wherein the thrust bearing and all the radial bearings can be disposed entirely in the first casing (which can be understood as a motor casing), and no bearing needs to be disposed in the second casing (which can be understood as a gas turbine casing). Like this, only need guarantee in the first casket be used for setting up the machining precision at the position of bearing stator can, the position that is used for connecting the bearing stator in the first casket when the assembly can be accomplished through the processing of once installing the card, it is visible, the utility model discloses reduce the machining precision and the assembly precision of gas turbine generator system, the cost is reduced is fit for engineering batch production.

The embodiment of the utility model provides an in, the pivot can the level setting, also can vertical setting, consequently, can understand ground, the utility model discloses rotor system both has been applicable to the horizontal unit that needs use rotor system, also is applicable to the vertical unit that needs use rotor system, for example horizontal gas turbine motor group, or vertical gas turbine motor group.

The embodiment of the utility model provides an in, because the axis body structure as an organic whole of pivot to adopt the shaft coupling to be connected gas turbine rotor and electric motor rotor among the difference in prior art. Compared with the prior art, because the axis body of pivot is structure as an organic whole, the intensity of the axis body everywhere in the pivot has the uniformity, and this makes thrust bearing unrestricted in the epaxial position that sets up of pivot.

The embodiment of the utility model provides an in, lean on the setting mutually through the impeller with the impeller of compressor and turbine for axial length in the first casket shortens, thereby can further improve whole rotor system's stability.

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

As shown in fig. 15, an embodiment of the present invention provides a rotor system, which includes a rotating shaft 100 and a thrust bearing 500, wherein a shaft body of the rotating shaft 100 is an integral structure, and the rotating shaft 100 is horizontally disposed;

the motor 200, the compressor 300, the turbine 400, the thrust bearing 500, the first radial bearing 600 and the second radial bearing 700 are arranged on the rotating shaft 100, the first radial bearing 600 and the second radial bearing 700 are non-contact bearings, and the first radial bearing 600 and the thrust bearing 500 are integrated into a whole to form an integrated bearing 10000;

and a first casing 800 and a second casing 900, the first casing 800 being connected to the second casing 900, wherein the motor 200, the thrust bearing 500, the first radial bearing 600, and the second radial bearing 700 are all disposed in the first casing 800, and the compressor 300 and the turbine 400 are all disposed in the second casing 900.

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

Therefore, in consideration of the development requirement of the high rotation speed of the gas turbine generator set, in order to improve the working performance of the thrust bearing and the radial bearing, in the embodiment of the present invention, the first radial bearing 600 may adopt a gas-magnetic hybrid radial bearing or a gas hybrid radial bearing; the second radial bearing 700 may employ a gas-magnetic hybrid radial bearing or a gas hybrid radial bearing.

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

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

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

Further, the motor 200 may also be a starter-integral motor.

Thus, at the initial starting time of the rotor system, the motor 200 may be started in the starting mode to rotate the rotor system, and after the rotation speed of the rotor system is increased to the preset rotation speed, the working mode of the motor 200 may be switched to the power generation mode.

As shown in fig. 16, an embodiment of the present invention provides another rotor system, which includes a rotating shaft 100 and a thrust bearing 500, wherein a shaft body of the rotating shaft 100 is an integral structure, and the rotating shaft 100 is vertically disposed;

All the other can refer to the relevant description in fig. 11 to can reach the same technical effect, in order to avoid repetition, the embodiment of the present invention is not repeated to this.

EXAMPLE five

When the rotor system of the present application is used on a mobile device, such as an extended range electric vehicle, the shaft is in direct contact with the bearing when the rotor system is not in operation. When the automobile runs, the rotating shaft moves relative to the bearing in the radial direction or the axial direction due to bumping or vibration, so that abrasion is generated between the rotating shaft and the bearing, and the precision and the service life of the bearing are further influenced.

Therefore, in order to solve the above problem, the utility model discloses on the basis of other embodiments, the utility model discloses a rotor system sets up locking device, and this locking device is used for when rotor system is out of work, locks the pivot.

In the embodiment of the present invention, the structural form and the arrangement of the locking device are not exclusive, and for easy understanding, two embodiments of the locking device provided in the rotor system will be specifically described below with reference to fig. 9.

In one embodiment, as shown in fig. 17, the locking device 110 includes a telescopic tightening unit 111, a connecting rod 112 and a fixing part 113, one end of the connecting rod 112 is connected to the fixing part 113, the other end is connected to the telescopic tightening unit 111, the telescopic tightening unit 111 faces an end surface of the rotating shaft 100 far away from the end of the turbine 400, and the other end of the fixing part 113 is fixedly connected to a housing for mounting the rotor system of the present application.

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 with the thrust disc, thereby axially fixing the rotating shaft 100, and simultaneously radially fixing the rotating shaft 100 by using the friction force between the stator of the thrust bearing 500 and the thrust disc.

Further, the telescopic tightening unit 111 is provided with a tip portion (not shown), and an end surface of the rotating shaft 100 at an end far from the turbine 400 is provided with a tip hole (not shown). In the locked state, the apex portion pushes into the apex hole of the rotating shaft 100, so that the rotating shaft 100 can be better fixed, and the rotating shaft 100 and the bearing are prevented from being worn and damaged in the driving process of the vehicle.

In another embodiment, as shown in fig. 18-19, the locking device 120 may also be configured as a ferrule-based locking device. Specifically, the locking device 120 includes a telescopic unit 121 and a ferrule 122, and the ferrule 122 is coupled to a 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 rotary shaft 100, the axis of the ferrule 122 is disposed in parallel with the axis of the rotary shaft 100, and the telescopic unit 121 is mounted to a substantially axial middle position of the rotary shaft 100 and is fixedly connected to a housing in which the rotor system of the present application is mounted.

When the rotor system is stopped, the telescopic unit 121 is extended to make the ferrule 122 seize the rotating shaft 100 and push the rotating shaft 100 to contact with the radial bearing, thereby radially fixing the rotating shaft 100 and axially fixing the rotating shaft 100 by using the friction force of the radial bearing and the rotating shaft 100.

Further, the telescopic unit 121 may be a piston cylinder or a hydraulic cylinder, which can perform telescopic control.

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

It should be noted that the locking devices in fig. 17 and 18 are both based on the rotor system configuration shown in fig. 13, and the locking devices provided in the rotor systems according to other embodiments of the present invention are not described one by one here.

The embodiment of the utility model provides an in, through setting up locking device, when rotor system is out of work, locking device can lock the pivot. Thus, the rotation shaft can be prevented from moving in the radial direction or the axial direction with respect to the bearing, and the accuracy and the life of the bearing can be improved.

EXAMPLE six

Therefore, in order to solve the above problem, on the basis of other embodiments of the present invention, the rotor system of the embodiment of the present invention is coated with an anti-wear coating 101 at the bearing-mounting portion of the rotating shaft 100, as shown in fig. 19.

The anti-abrasion coating 101 is coated on the part of the rotating shaft 100 where the bearing is installed, so that the abrasion of the rotating shaft 100 and the bearing can be effectively prevented. The wear-resistant coating 101 is preferably a chemically stable, corrosion resistant, highly lubricious non-stick and good resistance to aging, such as polytetrafluoroethylene.

It should be noted that the wear-resistant coating 101 in fig. 19 is based on the rotor system configuration shown in fig. 13, and no description is made here for providing the locking device in the rotor system according to other embodiments of the present invention.

EXAMPLE seven

A method for controlling a bearing (in which the first magnetic member in the first magnetic bearing is a first electromagnet and the second magnetic member in the second magnetic bearing is a second electromagnet) in a rotor system according to an embodiment of the present invention will be described in detail below.

As shown in fig. 21, an embodiment of the present invention provides a bearing control method, including:

s1011, starting the first magnetic bearing and the second magnetic bearing.

S1012, controlling the rotating shaft to move in the radial direction of the rotating shaft under the action of the magnetic force of the first magnetic parts so as to enable the rotating shaft to move to a preset radial position; and controlling the thrust disc to move in the axial direction of the rotating shaft by a magnetic force between the plurality of second magnetic members and the third magnetic member so that a difference between a second gap between the thrust disc and the second magnetic bearing of the first stator and a second gap between the thrust disc and the second magnetic bearing of the second stator is less than or equal to a predetermined value.

And S1013, after the rotating speed of the rotating shaft is accelerated to the working rotating speed, closing the first magnetic bearing and the second magnetic bearing.

And S1014, when the rotor system is stopped, starting the first magnetic bearing and the second magnetic bearing.

And S1015, closing the first magnetic bearing and the second magnetic bearing after the rotating speed of the rotating shaft is reduced to zero.

In the above process, after the first magnetic bearing and the second magnetic bearing are turned on, the rotating shaft is supported by the plurality of first magnetic members and reaches a preset radial position (the radial position of the rotating shaft can be detected by the displacement sensor), and the thrust disc reaches a predetermined position between the first stator and the second stator by the magnetic force between the plurality of second magnetic members and the third magnetic member. As the rotating shaft rotates, the rotating shaft starts rotating while being lubricated by the air flow in the first gap to prevent wear; the thrust disc starts to rotate relative to the first stator and the second stator under lubrication by the air flow in the second gap to prevent wear.

The specific process of starting the first magnetic bearing and the second magnetic bearing is as follows: a current signal of a predetermined value is input to the first coil and the second coil.

With the increasing of the rotating speed of the rotating shaft, when the rotating speed of the rotating shaft reaches the working rotating speed, the rotating shaft and the thrust disc can be stabilized by the gas film pressure generated by the gas dynamic pressure bearings (the first gap is arranged between the first magnetic bearing and the rotating shaft, namely the gas dynamic pressure bearing forming the radial sub-bearing, and the second gap is arranged between the thrust disc and the stator, namely the gas dynamic pressure bearing forming the thrust sub-bearing) of the radial sub-bearing and the thrust sub-bearing, and then the first magnetic bearing and the second magnetic bearing can be closed.

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

As shown in fig. 22, an embodiment of the present invention further provides another bearing control method, including:

s1021, starting the first magnetic bearing and the second magnetic bearing.

S1022, controlling the rotating shaft to move in the radial direction of the rotating shaft under the action of the magnetic force of the first magnetic components, so that the rotating shaft moves to a preset radial position; and controlling the thrust disc to move in the axial direction of the rotating shaft by a magnetic force between the plurality of second magnetic members and the third magnetic member so that a difference between a second gap between the thrust disc and the second magnetic bearing of the first stator and a second gap between the thrust disc and the second magnetic bearing of the second stator is less than or equal to a predetermined value.

And S1023, after the rotating speed of the rotating shaft is accelerated to a first preset value, closing the first magnetic bearing and the second magnetic bearing.

And S1024, starting the first magnetic bearing and the second magnetic bearing when the rotor system is accelerated to the first-order critical speed or the second-order critical speed.

Specifically, when the gas flow rate in the first gap between the rotating shaft and the first magnetic bearing reaches a first-order critical speed or a second-order critical speed, the first magnetic bearing and the second magnetic bearing are started until the rotating shaft returns to an equilibrium position.

Optionally, when the rotor system accelerates to a first-order critical speed or a second-order critical speed, the first magnetic bearing and the second magnetic bearing are turned on, including:

when the rotor system accelerates to a first-order critical speed or a second-order critical speed, the first magnetic bearing and the second magnetic bearing are controlled to be started at the maximum power; or,

and when the rotor system accelerates to a first-order critical speed or a second-order critical speed, controlling the first magnetic bearing and the second magnetic bearing to be started in a stroboscopic mode according to a preset frequency.

And S1025, after the rotor system passes through the first-order critical speed or the second-order critical speed in a smooth mode, closing the first magnetic bearing and the second magnetic bearing.

And S1026, in the process of stopping the rotor system, when the rotor system decelerates to a first-order critical speed or a second-order critical speed, starting the first magnetic bearing and the second magnetic bearing.

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

Optionally, when the rotor system decelerates to the first-order critical speed or the second-order critical speed, the first magnetic bearing and the second magnetic bearing are turned on, including:

when the rotor system decelerates to a first-order critical speed or a second-order critical speed, the first magnetic bearing and the second magnetic bearing are controlled to be started at the maximum power; or,

and when the rotor system decelerates to a first-order critical speed or a second-order critical speed, controlling the first magnetic bearing and the second magnetic bearing to be started in a stroboscopic mode according to a preset frequency.

S1027, after the rotor system passes the first-order critical speed or the second-order critical speed, the first magnetic bearing and the second magnetic bearing are closed.

S1028, when the rotating speed of the rotating shaft is reduced to a second preset value, the first magnetic bearing and the second magnetic bearing are started.

S1029, after the rotating speed of the rotating shaft is reduced to zero, the first magnetic bearing and the second magnetic bearing are closed.

As the rotating speed of the rotating shaft is increased, when the rotating speed of the rotating shaft reaches a first preset value, for example, 5% to 30% of the rated rotating speed, the rotating shaft and the thrust disc can be stabilized by the gas film pressure generated by the gas dynamic bearings of the radial sub-bearing and the thrust sub-bearing (the gas dynamic bearing forming the radial sub-bearing is provided with a first gap between the first magnetic bearing and the rotating shaft, and the gas dynamic bearing forming the thrust sub-bearing is provided with a second gap between the thrust disc and the stator), and then the first magnetic bearing and the second magnetic bearing can be closed.

During the shutdown of the rotor system, the rotation speed of the rotating shaft is gradually reduced, and when the rotation speed of the rotating shaft is lower than a second preset value, for example, 5% to 30% of the rated rotation speed, at this time, the air film pressure generated by the aerodynamic bearings of the radial sub-bearing and the thrust sub-bearing is also reduced along with the deceleration of the rotating shaft or the thrust disc, so that the first magnetic bearing and the second magnetic bearing need to be opened to keep the rotating shaft and the thrust disc stable, and the first magnetic bearing and the second magnetic bearing can be closed until the speed of the rotating shaft is zero.

Optionally, the method further includes:

when a first gap between the rotating shaft and the first magnetic bearing is changed, the first magnetic bearing is started, and the rotating shaft moves towards the direction away from the gap reducing side under the action of the magnetic force of the plurality of first magnetic components;

after the shaft is in the equilibrium radial position, the first magnetic bearing is turned off.

When a load is loaded on the rotating shaft, so that the rotating shaft gradually descends and approaches the first magnetic bearing below, the first sensor (the first sensor is preferably a pressure sensor) obtains a signal of air pressure increase, and the first magnetic bearing needs to be operated in an intervening mode. The first magnetic bearing acts magnetic force on the rotating shaft to make the rotating shaft float upwards, and when the rotating shaft reaches a new balance radial position, the first magnetic bearing stops working.

When external impact disturbance occurs, the rotating shaft may rapidly approach the first magnetic bearing, which may cause the instant over-small of the first gap between the rotating shaft and the first magnetic bearing, so that the local gas flow velocity at the reduced position of the first gap approaches or even reaches the sonic velocity, thereby causing shock wave to generate air hammer self-excitation. The generation of the shock wave causes turbulence and chaos in the local gas flow, with the pressure dropping dramatically in steps as the fluid velocity changes from sonic to subsonic. In this case, the first magnetic components of the first magnetic bearing need to be controlled to be turned on in turn at a preset frequency so as to provide a damping effect on the disturbance, thereby effectively suppressing the external disturbance. The first magnetic bearing ceases operation after the shaft has returned to the new equilibrium radial position.

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

Optionally, the method further includes:

when a load is loaded on the thrust disc, the thrust disc moves in the axial direction of the rotating shaft under the action of the load, and the difference value between a second gap between the thrust disc and a second magnetic bearing in the first stator and a second gap between the thrust disc and a second magnetic bearing in the second stator is larger than a preset value, the second magnetic bearing is started;

and when the difference value between the second gap between the thrust disc and the second magnetic bearing in the first stator and the second gap between the thrust disc and the second magnetic bearing in the second stator is less than or equal to a preset value, closing the second magnetic bearing.

When a load is applied to the thrust disk and a second gap between the thrust disk and the second magnetic bearing of the first stator or the second stator becomes smaller and approaches the second magnetic bearing on the side, the second sensor (here, the second sensor is preferably a pressure sensor) obtains a signal of an increase in air pressure, and the second magnetic bearing needs to be operated. The second magnetic bearing acts magnetic force on the thrust disc to move the thrust disc to the second magnetic bearing on the other side, and when the thrust disc reaches a new balance position, the second magnetic bearing can stop working.

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

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

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

when a load is loaded on the thrust disc, the thrust disc moves in the axial direction of the rotating shaft under the action of the load, and the difference value between a second gap between the thrust disc and a second magnetic bearing in the first stator and a second gap between the thrust disc and a second magnetic bearing in the second stator is larger than a preset value, controlling the second magnetic bearing in the first stator or the second stator to be started at the maximum power; or,

and when the load is loaded on the thrust disc, the thrust disc moves in the axial direction of the rotating shaft under the action of the load, and the difference value between a second gap between the thrust disc and the second magnetic bearing in the first stator and a second gap between the thrust disc and the second magnetic bearing in the second stator is greater than a preset value, controlling the second magnetic bearing in the first stator or the second stator to be started in a stroboscopic mode according to preset frequency.

When external impact disturbance occurs, the thrust disc can be quickly close to a second magnetic bearing on one side, so that the second gap on the side is instantaneously too small, the local gas flow velocity at the second gap on the side is close to or even reaches the sonic velocity, and the shock wave is caused to generate the air hammer self-excitation phenomenon. The generation of the shock wave causes turbulence and chaos in the local gas flow, with the pressure dropping dramatically in steps as the fluid velocity changes from sonic to subsonic. In this case, it is necessary to control the second magnetic bearings in the first stator and the second stator to be alternately turned on at a preset frequency to provide a damping effect on the disturbance, so as to effectively suppress the external disturbance. When the thrust disc returns to the equilibrium state, the second magnetic bearing stops working.

In the process, the thrust disc is fixed in a certain minimum range in the axial direction of the rotating shaft by utilizing the advantage that the second magnetic bearing is convenient to control in real time and actively balancing the unbalanced mass of the thrust disc or the factors causing excessive deviation of the thrust disc such as the vortex motion of the thrust disc. In addition, in the acceleration process of the thrust disc, the position (namely the linear velocity supersonic speed position) generating the shock wave can be accurately positioned, and the second magnetic bearing generates opposite force to balance the shock wave action by controlling the current magnitude, the current direction and the like of the second magnetic bearing. After the shock wave is stable, the control strategy of the second magnetic bearing is adjusted again, and the thrust disc is fixed in a certain minimum range in the most energy-saving mode.

The embodiment of the utility model provides an in, be provided with the magnetic bearing simultaneously to the bearing (wherein, the first magnetic part in the first magnetic bearing is first electro-magnet, and the second magnetic part in the second magnetic bearing is the second electro-magnet) and the condition of gas hydrostatic bearing (be provided with static pressure intake orifice on the bearing shell), magnetic bearing and gas hydrostatic bearing can be mutual reserve, under the condition that one of them side trouble, became invalid or can't satisfy the condition of opening, the other side can play the same effect as reserve bearing. For example, in case of detecting the failure of the magnetic bearing, the external air source is controlled to be opened to perform corresponding actions instead of the magnetic bearing, thereby improving the safety and reliability of the bearing.

Specifically, the following embodiments may be included:

when the first magnetic bearing and the second magnetic bearing are in a fault state, starting an external air source, and conveying air to the first gap and the second gap through the static pressure air inlet throttling hole;

controlling the rotating shaft to move along the radial direction of the rotating shaft under the action of the gas so as to enable the rotating shaft to move to a preset radial position; and controlling the thrust disc to move in an axial direction of the rotating shaft under the action of the gas such that the second gap between the thrust disc and a second magnetic bearing of the first stator is equal to the second gap between the thrust disc and a second magnetic bearing of the second stator.

The above-described embodiment corresponds to a method for controlling a bearing when the first and second magnetic bearings are in a failure state during a start-up phase of the rotor system. For the control method of other stages of the rotor system, the control of the bearings can be realized by turning on or off the external air source, which is not described in detail because it is easy to understand.

Optionally, the step of turning on the first and second magnetic bearings when the first and second magnetic bearings are in a normal state includes:

when the first magnetic bearing and the second magnetic bearing are in a normal state, the first magnetic bearing and the second magnetic bearing are started, an external air source is started, and air is conveyed to the first gap and the second gap through the static pressure air inlet throttling hole;

the rotating shaft is controlled to move in the radial direction of the rotating shaft under the action of the magnetic force of the plurality of first magnetic components, so that the rotating shaft is moved to a preset radial position; and a step of controlling the thrust disk to move in the axial direction of the rotating shaft by a magnetic force between the plurality of second magnetic members and the third magnetic member so that the second gap between the thrust disk and a second magnetic bearing of the first stator is equal to the second gap between the thrust disk and a second magnetic bearing of the second stator, including:

controlling the rotating shaft to move in the radial direction of the rotating shaft under the action of the magnetic force of the plurality of first magnetic components and the action of gas so as to enable the rotating shaft to move to a preset radial position; and controlling the thrust disk to move in the axial direction of the rotating shaft by a magnetic action between the plurality of second magnetic members and the third magnetic member and by a gas so that the second gap between the thrust disk and a second magnetic bearing of the first stator is equal to the second gap between the thrust disk and a second magnetic bearing of the second stator.

Like this, through the embodiment that adopts magnetic bearing and aerostatic bearing open simultaneously, can further improve the utility model discloses the bearing capacity of the bearing of embodiment.

In addition, when the magnetic bearing is in a normal state, only the aerostatic bearing can be started, and the details are not described for easy understanding.

In summary, the preferred embodiment of the present invention has the following advantages:

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

And secondly, mix the radial subbearing for the traditional gas dynamic and static pressure that adopts aerostatic bearing and gas dynamic pressure bearing to combine, the utility model discloses the radial subbearing has the fast advantage of response speed.

And thirdly, the gas hydrostatic bearing is added to form a hybrid dynamic-static-magnetic radial sub-bearing, under the condition that the magnetic bearing and the gas hydrostatic bearing are arranged at the same time, the bearing capacity of the bearing is further increased, the magnetic bearing and the gas hydrostatic bearing can be mutually standby, and under the condition that one of the magnetic bearing and the gas hydrostatic bearing fails, the other one of the magnetic bearing and the gas hydrostatic bearing can serve as a standby bearing to play the same role. For example, in case of detecting a failure of the magnetic bearing, the control system controls the aerostatic bearing to be opened to perform a corresponding action instead of the magnetic bearing, thereby improving the safety and reliability of the bearing.

In the present application, the radial bearing (for example, the second radial bearing 700 shown in fig. 13) separately provided in the rotor system may adopt various structural forms, and if the radial bearing adopts a hybrid gas-magnetic radial bearing, the radial bearing may be a foil type hybrid gas-magnetic radial bearing, or a groove type hybrid gas-magnetic radial bearing.

The specific structural forms of the two radial bearings and the specific control processes in the control of the entire rotor system are described in detail below with reference to the accompanying drawings.

Example eight

Fig. 23 to fig. 30 are schematic structural views of a foil type gas-magnetic hybrid radial bearing provided in an embodiment of the present invention.

As shown in fig. 23 to 30, the foil type gas-magnetic hybrid radial bearing 6100 includes:

a third magnetic bearing 6101 sleeved on the rotating shaft 100, wherein a plurality of fifth magnetic components are arranged on the third magnetic bearing 6101 along the circumferential direction;

a second foil bearing 6102 sleeved on the rotation shaft 100 and located between the third magnetic bearing 6101 and the rotation shaft 100, wherein the second foil bearing 6102 is provided with a sixth magnetic component capable of generating magnetic force with the plurality of fifth magnetic components;

a third gap 6103 is formed between the second foil bearing 6102 and the rotating shaft 100, and the second foil bearing 6102 can move in the radial direction of the rotating shaft 100 under the magnetic force of the fifth and sixth magnetic components.

In the embodiment of the present invention, the third gap 6103 and the third magnetic bearing 6101 are provided in the radial bearing 6100, so that the radial bearing 6100 forms a gas-magnetic hybrid radial bearing.

When the radial bearing 6100 works, the gas bearing in the radial bearing 6100 and the third magnetic bearing 6101 can work cooperatively, and when the radial bearing 6100 is in a stable working state, the gas bearing is relied on to realize support; when the radial bearing 6100 is in an unstable working state, the radial bearing 6100 is controlled and responded in time by the third magnetic bearing 6101.

It is visible, the embodiment of the utility model provides a can improve journal bearing, especially dynamic property and stability under high-speed running state, the anti disturbance ability reinforce, and then has improved journal bearing's bearing capacity. The utility model discloses radial bearing can satisfy the rotor system of high rotational speed, for example, the demand of gas turbine or gas turbine power generation combined unit etc..

In the embodiment of the present invention, 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 can be formed by laminating a plurality of silicon steel sheets or silicon steel sheets.

Optionally, the plurality of fifth magnetic components include a plurality of third permanent magnets, which are circumferentially disposed on the third magnetic bearing 6101;

alternatively, the plurality of fifth magnetic members include a plurality of third electromagnets, the plurality of third electromagnets are circumferentially disposed on the third magnetic bearing 6101, and each of the plurality of third electromagnets includes a third magnetic core 61011 disposed on the third magnetic bearing 6101 and a third coil 61012 wound around the third magnetic core 61011.

In the embodiment of the present invention, when the foil-type gas-magnetic hybrid radial bearing 6100 only requires the magnetic component to provide magnetic force and does not require magnetic control, the fifth magnetic component is preferably a third permanent magnet; when the foil gas-magnetic hybrid thrust bearing requires both magnetic force and magnetic control, the fifth magnetic component is preferably a third electromagnet.

When the fifth magnetic component is the third electromagnet, a current is applied to the third coil 61012, so that the third magnetic core 61011 generates a magnetic force. The magnitude of the current flowing into the third coil 61012 is different, and the magnitude of the magnetic force generated by the third magnetic core 61011 is also different; the direction of current flowing to the third coil 61012 is different, and the magnetic pole of the third core 61011 is also different.

Wherein, because silicon steel sheet or silicon steel sheet have physical properties such as magnetic permeability height, eddy current loss low, the utility model discloses a preferred embodiment, third magnetic core 61011 can be laminated by a plurality of silicon steel sheets or silicon steel sheet and become.

Optionally, the third magnetic bearing 6101 includes:

a third magnetic bearing base 61013, wherein the third magnetic bearing base 61013 is sleeved on the rotating shaft 100, a plurality of third receiving grooves 61014 are formed in the third magnetic bearing base 61013 along the circumferential direction, a plurality of fifth magnetic components are disposed in the plurality of third receiving grooves 61014, and magnetic poles of the plurality of fifth magnetic components face to the side where the second foil bearing 6102 is located;

a first housing 61015 disposed outside the third magnetic bearing base 61013;

a first bearing housing 61016 disposed between the third magnetic bearing pedestal 61013 and the second foil bearing 6102;

and a third end cap 61017 and a fourth end cap 61018 respectively disposed at two ends of the first bearing housing 61015;

the first housing 61016, the third end cap 61017, and the fourth end cap 61018 cooperate to fix the fifth magnetic members to the third magnetic bearing base 61013.

Wherein, because the silicon steel sheet or the silicon steel sheet have physical properties such as high permeability, low eddy current loss, etc., in the preferred embodiment of the present invention, the third magnetic bearing base 61013 can be formed by laminating a plurality of silicon steel sheets or silicon steel sheets. The number of the third receiving grooves 61014 may be, but is not limited to, six or eight, and is uniformly arranged along the circumferential direction of the third magnetic bearing housing 61013. In this way, the magnetic force between the third magnetic bearing 6101 and the second foil bearing 6102 can be made more uniform and stable. The plurality of fifth magnetic members may be provided on the third magnetic bearing base 61013 in another manner, which is not limited to this. The material of the third 61017 and fourth 61018 end caps may be non-magnetic, preferably duralumin. The material of the first bearing housing 61016 may be a non-magnetic material, preferably a duralumin material. The material of the first bearing housing 61015 may be a non-magnetic material, preferably a duralumin material.

Optionally, the second foil bearing 6102 includes a third foil 61021 and a fourth foil 61022, the third foil 61021 is mounted on the first bearing housing 61016, and the fourth foil 61022 is stacked on one side of the third foil 61021 close to the rotating shaft 100;

wherein, the fourth foil 61022 is a flat foil, and the sixth magnetic element is disposed on the fourth foil 61022, so that the fourth foil 61022 can move in the radial direction of the rotating shaft 100 under the magnetic force of the plurality of fifth magnetic elements and the sixth magnetic element; the third foil 61021 is an elastically deformable foil that can be elastically deformed when the fourth foil 61022 is moved.

Among them, the third foil 61021 is an elastically deformable foil, and it is not preferable to use the elastically deformable foil because the material of the magnetic conductive material is hard and brittle, and therefore, the third foil 61021 is preferably a stainless steel band which is not magnetically conductive.

In the embodiment of the present invention, by setting the fourth foil 61022 to be a flat foil, it is convenient to control the distance between the fourth foil 61022 and the rotating shaft 100, or to control the size of the third gap 6103.

Optionally, the third foil 61021 is a wavy elastic deformation foil, and the third foil 61021 is an unclosed ring shape, and is provided with an opening, one end of the opening is a fixed end, the fixed end is fixed on the first bearing sleeve 61016, and the other end of the opening is a movable end;

when the fourth foil 61022 moves in the radial direction of the rotating shaft 100, the wave patterns on the third foil 61021 extend or contract, and the movable end moves along the annular circumferential direction.

In the embodiment of the present invention, the third foil 61021 is set to be a wavy elastic deformation foil, so that the fourth foil 61022 is pushed to move in the radial direction of the rotating shaft 100 by utilizing the expansion or contraction characteristics of the wavy lines.

It should be noted that the shape of the third foil 61021 in the embodiment of the present invention is not limited to the wave shape, and other shapes that can generate elastic deformation may be applied to the third foil 61021 in the embodiment of the present invention.

Optionally, the sixth magnetic component includes a third magnetic material 61023 disposed on a side surface of the fourth foil 61022 near the first bearing housing 61016;

wherein, the third magnetic material 61023 is distributed on the fourth foil 61022 in a strip shape to form a plurality of strip-shaped magnetic portions, and the length direction of the plurality of strip-shaped magnetic portions is parallel to the axial direction of the rotating shaft 100;

alternatively, the third magnetic elements are distributed in dots on the fourth foil 61022.

Wherein the material of the fourth foil 61022 is preferably non-magnetic conductive material, after the third magnetic material 61023 is sprayed on the surface of the fourth foil 61022, the third magnetic material 61023 may be covered with a ceramic coating, the fourth foil 61022 may be made by sintering ceramic nanopowder using 40% zirconia, 30% α alumina and 30% magnesium aluminate spinel.

If the surface of the fourth foil 61022 completely covers the third magnetic material 61023, the magnetic force generated between the third magnetic material 61023 and the first magnetic component is greatly increased, which easily causes the fourth foil 61022 to deform. In view of this, in the embodiment of the present invention, the third magnetic material 61023 is sprayed on the surface of the fourth foil 61022, so that the third magnetic material 61023 is distributed on the fourth foil 61022 in a stripe shape or a dot shape, and the magnetic force generated between the third magnetic material 61023 and the first magnetic component can be controlled within a reasonable range, thereby preventing the fourth foil 61022 from being deformed due to an excessive magnetic force.

Optionally, the foil-type air-magnetic hybrid radial bearing 6100 further includes a plurality of third sensors 6104 disposed at intervals in the circumferential direction of the third magnetic bearing 6101, where each of the third sensors 6104 includes a third sensor cover 61041 and a third sensor probe 61042, a first end of the third sensor probe 61042 is connected to the third sensor cover 61041, the third sensor cover 61041 is fixed to the third magnetic bearing 6101, and through holes for the third sensor probe 61042 to pass through are disposed on the first bearing housing 61015, the third magnetic bearing seat 61013, and the first bearing housing 61016; the second end of the third sensor probe 61042 passes through the through holes on the first bearing housing 61015, the third magnetic bearing holder 61013, and the first bearing housing 61016, and extends into the gap between the first bearing housing 61016 and the third foil 61021, and the second end of the third sensor probe 61042 is flush with the side of the first bearing housing 61016 close to the third foil 61021.

In the embodiment of the present invention, by providing the third sensor 6104, the gas pressure parameter at the third foil 61021 can be detected in real time. In this way, the third magnetic bearing 6101 can actively control the radial bearing 6100 based on the detection result of the third sensor 6104, and control can be performed with high accuracy.

In the embodiment of the present invention, the third sensor 6104 can be more stably disposed on the third magnetic bearing 6101 by the structural form and the installation manner of the third sensor 6104. In addition, the second end of the third sensor probe 61042 is flush with the side of the first bearing sleeve 61016 close to the third foil 61021, so that on one hand, the third sensor probe 61042 can be prevented from being touched by the third foil 61021, and therefore, the third sensor probe 61042 can be protected; on the other hand, the air film in the third gap 6103 is not affected, and disturbance of the air film in the third gap 6103 is avoided.

Optionally, in the plurality of third sensors 6104, each third sensor 6104 is disposed between two adjacent fifth magnetic components.

In the embodiment of the present invention, the number of the third sensors 6104 may be the same as the number of the fifth magnetic components, each of the third sensors 6104 is disposed between two adjacent fifth magnetic components, and each of the third sensors 6104 is preferably disposed in the middle of the third magnetic bearing 6101. Furthermore, in the embodiment of the present invention, besides the third sensor 6104 for detecting the gas pressure parameter at the third foil 61021, a displacement sensor for detecting the position of the rotating shaft, or a speed sensor for detecting the rotating speed of the rotating shaft, or an acceleration sensor for detecting the rotating acceleration of the rotating shaft, etc. may be further provided.

The following describes in detail a specific control method of the foil gas-magnetic hybrid radial bearing (in which the fifth magnetic component in the third magnetic bearing is an electromagnet) according to an embodiment of the present invention, in the case where the foil gas-magnetic hybrid radial bearing participates in the control process of the rotor system.

The embodiment of the utility model provides a control method of foil formula gas magnetism mixing journal bearing, include:

and S611, starting the third magnetic bearing, and controlling the rotating shaft to move in the radial direction of the rotating shaft under the magnetic force action of the fifth magnetic components so as to enable the rotating shaft to move to a preset radial position.

And S612, after the rotating speed of the rotating shaft is accelerated to the working rotating speed, closing the third magnetic bearing.

And S613, starting the third magnetic bearing when the rotor system is stopped.

And S614, closing the third magnetic bearing after the rotating speed of the rotating shaft is reduced to zero.

In the above process, after the third magnetic bearing is opened, the rotating shaft is supported under the action of the third magnetic bearing and reaches the preset position, and a third gap is formed between the second foil bearing and the rotating shaft.

As the rotating shaft rotates, the rotating shaft starts rotating while being lubricated by the air flow in the third gap to prevent wear. The specific process of opening the third magnetic bearing is as follows: and a current signal with a preset value is input to the third coil, and the rotating shaft is supported and reaches a preset position under the action of the third magnetic bearing.

With the increasing rotation speed of the rotating shaft, when the rotation speed of the rotating shaft reaches the working rotation speed, the rotating shaft can be stabilized by the air film pressure generated by the aerodynamic bearing of the radial bearing (the third gap arranged between the second foil bearing and the rotating shaft forms the aerodynamic bearing of the radial bearing), and then the third magnetic bearing can be closed.

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

The embodiment of the utility model provides a still provide another kind of foil formula gas magnetism and mix radial bearing's control method, include:

and S621, starting the third magnetic bearing, and controlling the rotating shaft to move in the radial direction of the rotating shaft under the magnetic force action of the fifth magnetic parts so as to enable the rotating shaft to move to a preset radial position.

And S622, after the rotating speed of the rotating shaft is accelerated to a first preset value, closing the third magnetic bearing.

And S623, starting the third magnetic bearing when the rotating speed of the rotating shaft is accelerated to the first-order critical speed or the second-order critical speed.

Specifically, when the gas flow rate at the third gap between the rotating shaft and the second foil bearing (further, the fourth foil) reaches the first-order critical speed or the second-order critical speed, the third magnetic bearing is turned on until the rotating shaft returns to the equilibrium radial position.

Optionally, when the rotation speed of the rotating shaft is accelerated to the first-order critical speed or the second-order critical speed, the third magnetic bearing is turned on, including:

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

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

And S624, after the rotor system passes the first-order critical speed or the second-order critical speed, closing the third magnetic bearing.

And S625, in the process of stopping the rotor system, when the rotor system decelerates to the first-order critical speed or the second-order critical speed, starting a third magnetic bearing.

Specifically, when the gas flow speed at the third gap between the rotating shaft and the second foil bearing (further, the fourth foil) is decelerated to the first-order critical speed or the second-order critical speed, the third magnetic bearing is turned on until the rotating shaft is restored to the equilibrium radial position.

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

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

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

S626, turning off the third magnetic bearing after the rotor system steps through the first order critical speed or the second order critical speed.

And S627, when the rotating speed of the rotating shaft is reduced to a second preset value, starting the third magnetic bearing.

And S628, closing the third magnetic bearing after the rotating speed of the rotating shaft is reduced to zero.

As the rotating speed of the rotating shaft is increased, when the rotating speed of the rotating shaft reaches a first preset value, for example, 5% to 30% of the rated rotating speed, the rotating shaft can be stabilized by the air film pressure generated by the aerodynamic bearing of the radial bearing (the third gap provided between the second foil bearing and the rotating shaft, i.e., the aerodynamic bearing forming the radial bearing), and then the third magnetic bearing can be closed.

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

Optionally, the method further includes:

when a third gap between the rotating shaft and the second foil bearing (further, a fourth foil) is changed, the third magnetic bearing is turned on, so that the second foil bearing corresponding to the side with the smaller gap moves in a direction close to the rotating shaft under the action of the magnetic force between the fifth magnetic components and the sixth magnetic components;

the third magnetic bearing is turned off after the shaft is in an equilibrium radial position.

When a load is applied to the shaft, which is gradually lowered and approaches the fourth foil below, the third sensor (here, the third sensor is preferably a pressure sensor) obtains a signal of the increase of the air pressure, and the third magnetic bearing needs to be operated. The third magnetic bearing does not completely directly apply magnetic force to the rotating shaft to make the rotating shaft float upwards, but uses the magnetic force to push the fourth foil below upwards (i.e. towards the direction close to the rotating shaft), so that the lower gap is reduced, the pressure at the lower gap is increased, the third magnetic bearing adapts to the weight of the load on the rotating shaft, and the airflow pressure in all directions of the third gap is automatically redistributed. When the shaft reaches the new equilibrium radial position, the third magnetic bearing ceases to operate.

When external impact disturbance occurs, the rotating shaft may be quickly close to the second foil bearing, which may cause the gap between the rotating shaft and the second foil bearing to be instantaneously too small, so that the local gas flow velocity at the reduced gap is close to or even reaches the sonic velocity, thereby causing the shock wave to generate the self-excitation phenomenon of the air hammer. The generation of the shock wave causes turbulence and chaos in the local gas flow, with the pressure dropping dramatically in steps as the fluid velocity changes from sonic to subsonic. In this case, it is necessary to actively "back-off" the shaft with the second foil bearing so that the gap between the shaft and the second foil bearing is increased to maintain the gas velocity in the subsonic region as much as possible to maintain its normal fluid pressure. Specifically, the magnetic poles of the fifth magnetic members on the two opposite sides, which are required to change the gap, are excited with the same polarity, that is, the gap is decreased to generate an attraction force for attracting the second foil bearing, and the gap is increased to generate an attraction force for pulling the rotating shaft. Thus, the difference in magnetic force acting distance between the two sides is used to generate a difference in magnetic force, thereby pulling the rotating shaft to restore the normal clearance with the second foil bearing, thereby returning the rotating shaft to the new equilibrium radial position.

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

In conclusion, the embodiment of the utility model provides a following beneficial effect has:

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

And secondly, for the traditional gas hybrid thrust bearing that adopts aerostatic bearing and gas dynamic pressure bearing to combine, the utility model discloses the mixed journal bearing of paper tinsel formula gas magnetism has the fast advantage of response speed.

Thirdly, the magnetic material is arranged on the foil, the foil can be properly deformed through the attraction of the magnetic pole of the electromagnetic bearing, the highest pressure of one side of a lubricating air film in the bearing is improved, the lubricating air flow is prevented from leaking, the capability of the thrust disc for resisting the disturbance eccentric wall collision is improved, and the bearing capacity of the bearing is improved.

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

Example nine

Fig. 31 to 38 are schematic structural views of a groove type air-magnetic hybrid radial bearing provided in an embodiment of the present invention.

As shown in fig. 31 to 38, the groove-type air-magnetic hybrid radial bearing 6200 includes:

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

a third dynamic pressure generating groove 6202 is provided on a side wall of the fourth magnetic bearing 6201 facing the rotating shaft 100, or on a circumferential surface of the rotating shaft 100 facing the fourth magnetic bearing 6201;

wherein, a fourth gap 6203 is provided between the fourth magnetic bearing 6201 and the rotating shaft 100, and the rotating shaft 100 can move in the radial direction of the rotating shaft 100 under the magnetic force of the seventh magnetic components.

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

When the radial bearing 6200 works, the gas bearing in the radial bearing 6200 and the fourth magnetic bearing 6201 can work cooperatively, and when the radial bearing 6200 is in a stable working state, the gas bearing is used for realizing support; and when the radial bearing 6200 is in an unstable working state, the radial bearing 6200 is controlled and responded by the fourth magnetic bearing 6201 in time.

In the embodiment of the present invention, 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, so that pressure is generated to float the rotating shaft 100, thereby realizing that the rotating shaft 100 is maintained in a non-contact manner along the radial direction. The pressure generated by the third dynamic pressure generating groove 6202 varies with the angle, groove width, groove length, groove depth, number of grooves, and flatness of the third dynamic pressure generating groove 6202. In addition, the magnitude of the pressure generated by the third dynamic pressure generating groove 6202 is also related to the rotation speed of the rotating shaft 100 and the fourth gap 6203. The parameters of the third dynamic pressure generating groove 6202 may be designed according to actual 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 members include a plurality of fourth permanent magnets, which are circumferentially disposed on the fourth magnetic bearing 6201;

alternatively, the plurality of seventh magnetic members include a plurality of fourth electromagnets disposed circumferentially 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 a fourth coil 62012 wound on the fourth magnetic core 62011.

In the embodiment of the present invention, when the groove-type air-magnetic hybrid radial bearing 6200 only needs the magnetic component to provide magnetic force and does not need magnetic control, the fourth permanent magnet is preferably selected as the seventh magnetic component; when the foil gas-magnetic hybrid thrust bearing requires both magnetic force and magnetic control, the seventh magnetic component is preferably a fourth electromagnet.

When the seventh magnetic element is the fourth electromagnet, a current is applied to the fourth coil 62012, so that the fourth magnetic core 62011 generates 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 magnetic core 62011 is also different; the direction of current flow to the fourth coil 62012 is different, and the magnetic pole of the fourth magnetic core 62011 is also different.

Wherein, because silicon steel sheet or silicon steel sheet have physical properties such as magnetic permeability height, eddy current loss low grade, the utility model discloses a preferred embodiment, fourth magnetic core 62011 can be laminated by a plurality of silicon steel sheets or silicon steel sheet and form.

Optionally, the fourth magnetic bearing 6201 includes:

a fourth magnetic bearing holder 62013, in which the fourth magnetic bearing holder 62013 is sleeved on the rotating shaft 100, a plurality of fourth accommodating grooves 62014 are circumferentially disposed on the fourth magnetic bearing holder 62013, a plurality of seventh magnetic members are disposed in the plurality of fourth accommodating grooves 62014, and magnetic poles of the plurality of seventh magnetic members face the rotating shaft 100;

a second bearing housing 62015 sleeved outside the fourth magnetic bearing seat 62013;

a second bearing cover 62016 sleeved between the fourth magnetic bearing pedestal 62013 and the rotating shaft 100;

and a fifth end cap 62017 and a sixth end cap 62018 disposed at both ends of the second bearing shell 62015, respectively;

the second bearing cover 62016, the fifth end cap 62017, and the sixth end cap 62018 cooperate to fix the seventh magnetic components to the fourth magnetic bearing seat 62013.

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

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

Wherein, because the silicon steel sheet or the silicon steel sheet have physical properties such as high magnetic permeability, low eddy current loss, etc., in the preferred embodiment of the present invention, the fourth magnetic bearing seat 62013 can be formed by laminating a plurality of silicon steel sheets or silicon steel sheets. The number of the fourth receiving grooves 62014 may be, but is not limited to, six or eight, which are uniformly arranged in the circumferential direction of the fourth magnetic bearing base 62013. In this way, the magnetic force between the fourth magnetic bearing 6201 and the rotating shaft 100 can be made more uniform and stable. The plurality of seventh magnetic members may be provided on the fourth magnetic bearing holder 62013 in another manner, which is not limited. The material of fifth end cap 62017 and sixth end cap 62018 may each be a non-magnetic material, preferably a duralumin material. The material of the second bearing cover 62016 may be a non-magnetic material, preferably a duralumin material. The material of the second bearing shell 62015 may be a non-magnetic material, preferably a duralumin material.

Preferably, the fifth end cap 62017 and the sixth end cap 62018 are provided with bosses having the same outer diameter as the inner diameter of the second bearing housing 62015, and the bosses of the fifth end cap 62017 and the sixth end cap 62018 are used for fixing and pressing silicon steel sheets or silicon steel sheets constituting the fourth magnetic bearing base 62013 from both ends.

The embodiment of the present invention provides a third dynamic pressure generating groove 6202 on the second bearing cover 62016, in order to facilitate the processing of the third dynamic pressure generating groove 6202, the second bearing cover 62016 may be made of a stainless steel material. Specifically, the third dynamic pressure generating grooves 6202 may be provided at a middle portion of the rotating shaft 100 corresponding to the circumferential surface of the second bearing sleeve 62016, or may be provided as two independent third dynamic pressure generating grooves 6202 symmetrically distributed at both sides of the middle portion; the third dynamic pressure generating grooves 6202 may be provided in a middle portion of an inner sidewall of the second bearing sleeve 62016, or may be provided as two independent portions of the third dynamic pressure generating grooves 6202 that are symmetrically distributed at both ends of the inner sidewall of the second bearing sleeve 62016.

Optionally, the third dynamic pressure generating grooves 6202 are arranged in a matrix, which is beneficial to more uniformly distributing the gas film in the fourth gap 6203.

Alternatively, the third dynamic pressure generating grooves 6202 are V-shaped grooves provided continuously or at intervals.

The embodiment of the present invention provides an embodiment, through the setting mode that adopts above-mentioned third dynamic pressure generating groove 6202, can be under the condition of pivot 100 forward rotation or reverse rotation, the pivot can both keep with mode non-contact ground of expectation to make pivot 100 have the advantage that the bearing capacity is high and stability is good. The third dynamic pressure generating grooves 6202 may be provided as chevron-shaped grooves or grooves of other shapes, in addition to the V-shaped grooves.

Optionally, a second static pressure intake orifice 6205 is also disposed on the fourth magnetic bearing 6201, one end of the second static pressure intake orifice 6205 is communicated with the fourth gap 6203, and the other end is connected to an external air source for delivering the external air source into the fourth gap 6203.

The embodiment of the utility model provides an in, through setting up above-mentioned second static pressure orifice 6205 that admits air, can form aerostatic bearing to this mixed journal bearing of slot type gas magnetism 6200 can constitute the mixed journal bearing of slot type gas static and dynamic pressure-magnetism. The flow diameter of the second static pressure air inlet throttle 6205 can be adjusted according to actual working conditions such as air quantity requirements and the like.

Optionally, the second static inlet orifice 6205 branches within the fourth magnetic bearing 6201 into a fourth gap 6203.

In embodiments of the present invention, the second static pressure 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 cover 62016 to communicate the external air source with the fourth gap 6203. Further, the second static pressure intake orifice 6205 may branch into two or more branches to the fourth gap 6203, so that the film pressure in the fourth gap 6203 is more uniform. Further, an annular groove may be provided in the fifth end cover 62017 or the sixth end cover 62018, and a plurality of second static pressure intake orifices 6205 may be provided in an annular region of the fourth magnetic bearing 6201 corresponding to the annular groove, for example, one second static pressure intake orifice 6205 may be provided in each fourth magnetic core 62011 or in each two adjacent fourth magnetic cores 62011. The flow diameters of the second static pressure intake orifice 6205 and the branch can be adjusted according to actual working conditions such as air quantity requirements.

Optionally, the slot-type gas-magnetic hybrid radial bearing 6200 further comprises a plurality of fourth sensors 6204 disposed circumferentially spaced apart along the fourth magnetic bearing 6201, wherein the sensor probe of each fourth sensor 6204 is disposed within the fourth gap 6203.

In the embodiment of the present invention, by providing the fourth sensor 6204, the parameter of the fourth gap 6203, for example, the air film pressure of the fourth gap 6203, can be detected in real time. In this way, the fourth magnetic bearing 6201 can actively control the radial bearing 6200 based on the detection result of the fourth sensor 6204, and can achieve high accuracy in control.

Optionally, each of the fourth sensors 6204 includes a fourth sensor cover 62041 and a fourth sensor probe 62042, the first end of the fourth sensor probe 62042 is connected to the fourth sensor cover 62041, the fourth sensor cover 62041 is fixed to the fourth magnetic bearing 6201, and a through hole for the fourth sensor probe 62042 to pass through is formed in the fourth magnetic bearing 6201; the second end of the fourth sensor probe 62042 passes through the through hole of the fourth magnetic bearing 6201 and extends to the fourth gap 6203, and the second end of the fourth sensor probe 62042 is flush with the side of the fourth magnetic bearing 6201 close to the rotating shaft 100.

In the embodiment of the present invention, the fourth sensor 6204 can be more stably disposed on the fourth magnetic bearing 6201 by the structural form and the installation manner of the fourth sensor 6204. In addition, the second end of the fourth sensor probe 62042 is flush with the side of the fourth magnetic bearing 6201 close to the rotating shaft 100, so that the fourth sensor probe 62042 can be prevented from being touched by the rotating shaft 100, and the fourth sensor probe 62042 can be protected; on the other hand, the air film in the fourth gap 6203 is not affected, and the air film in the fourth gap 6203 is prevented from being disturbed.

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

In an embodiment of the present invention, 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 two adjacent seventh magnetic members, or may pass through the seventh magnetic member, which is not limited in the embodiment of the present invention. Each fourth sensor 6204 is preferably disposed in a middle portion of the fourth magnetic bearing 6201.

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

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

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

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

The following describes in detail a specific control method of the embodiment of the present invention when the slot gas-magnetic hybrid radial bearing (in which, the seventh magnetic component in the fourth magnetic bearing is an electromagnet) participates in the control process of the rotor system.

The embodiment of the utility model provides a slot type gas-magnetic mixing radial bearing's control method, include:

and S631, starting the fourth magnetic bearing, controlling the rotating shaft to move in the radial direction of the rotating shaft under the magnetic force action of the seventh magnetic components, and pushing the rotating shaft to a preset radial position.

And S632, after the rotating speed of the rotating shaft is accelerated to the working rotating speed, closing the fourth magnetic bearing.

And S633, starting the fourth magnetic bearing when the rotor system is stopped.

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

In the process, after the fourth magnetic bearing is started, the rotating shaft is supported under the action of the fourth magnetic bearing and reaches the preset radial position, and a fourth gap is formed between the fourth magnetic bearing and the rotating shaft.

As the rotating shaft rotates, the rotating shaft starts rotating while being lubricated by the air flow in the fourth gap to prevent wear. The specific process of opening the fourth magnetic bearing is as follows: and a current signal with a preset value is input into the fourth coil, and the rotating shaft is supported under the action of the fourth magnetic bearing and reaches a preset radial position.

With the increasing rotation speed of the rotating shaft, when the rotation speed of the rotating shaft reaches the working rotation speed, the rotating shaft can be stabilized by the air film pressure generated by the aerodynamic bearing of the radial bearing (the fourth gap is arranged between the fourth magnetic bearing and the rotating shaft, namely the aerodynamic bearing of the radial bearing is formed), and then the fourth magnetic bearing can be closed.

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

The embodiment of the utility model provides a still provide another kind of slot type gas magnetism and mix radial bearing's control method, include:

and S641, starting the fourth magnetic bearing, controlling the rotating shaft to move in the radial direction of the rotating shaft under the magnetic force action of the seventh magnetic components, and pushing the rotating shaft to a preset radial position.

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

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

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

Optionally, when the rotation speed of the rotating shaft is accelerated to the first-order critical speed or the second-order critical speed, the fourth magnetic bearing is turned on, including:

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

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

S644, after the rotor system steps through the first-order critical speed or the second-order critical speed, the fourth magnetic bearing is turned off.

And S645, in the process of stopping the rotor system, when the rotor system decelerates to the first-order critical speed or the second-order critical speed, starting a fourth magnetic bearing.

Specifically, when the gas flow velocity in the fourth gap between the rotating shaft and the fourth magnetic bearing is reduced to the first-order critical velocity or the second-order critical velocity, the fourth magnetic bearing is turned on until the rotating shaft is restored to the equilibrium radial position.

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

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

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

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

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

And S648, closing the fourth magnetic bearing after the rotating speed of the rotating shaft is reduced to zero.

As the rotating speed of the rotating shaft is increased, when the rotating speed of the rotating shaft reaches a first preset value, for example, 5% to 30% of the rated rotating speed, the rotating shaft can be stabilized by the air film pressure generated by the aerodynamic bearing of the radial bearing (the aerodynamic bearing forming the radial bearing is provided with a fourth gap between the fourth magnetic bearing and the rotating shaft), and then the fourth magnetic bearing can be closed.

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

Optionally, the method further includes:

when a fourth gap between the rotating shaft and the fourth magnetic bearing is changed, the fourth magnetic bearing is started, and the rotating shaft moves towards a direction away from the gap reducing side under the action of the magnetic force of the seventh magnetic components;

the fourth magnetic bearing is turned off after the shaft is in an equilibrium radial position.

When a load is loaded on the rotating shaft, so that the rotating shaft gradually descends and approaches the lower fourth magnetic bearing, the fourth sensor (preferably a pressure sensor) obtains a signal of air pressure increase, and the fourth magnetic bearing needs to be operated in an intervening mode. The fourth magnetic bearing acts magnetic force on the rotating shaft to enable the rotating shaft to be suspended upwards, and when the rotating shaft reaches a new balance position, the fourth magnetic bearing stops working.

When external impact disturbance occurs, the rotating shaft can be fast close to the fourth magnetic bearing, which may cause the gap between the rotating shaft and the fourth magnetic bearing to be instantaneously too small, so that the local gas flow velocity at the gap reduction position is close to or even reaches the sonic velocity, thereby causing the shock wave to generate the self-excitation phenomenon of the air hammer. The generation of the shock wave causes turbulence and chaos in the local gas flow, with the pressure dropping dramatically in steps as the fluid velocity changes from sonic to subsonic. In this case, the seventh magnetic component of the fourth magnetic bearing needs to be controlled to be turned on in turn at a preset frequency to provide a damping effect on the disturbance, so as to effectively suppress the external disturbance. The fourth magnetic bearing ceases operation after the shaft has returned to the new equilibrium radial position.

It should be noted that, in the embodiment of the present invention, in the case where the electromagnetic bearing (the seventh magnetic component in the fourth magnetic bearing is an electromagnet, that is, an electromagnetic bearing is formed) and the aerostatic bearing (the second static pressure intake orifice provided in the fourth magnetic bearing is a aerostatic bearing) are provided at the same time, the electromagnetic bearing and the aerostatic bearing may be mutually standby, and in the case where one of the electromagnetic bearing and the aerostatic bearing fails, or cannot satisfy the opening condition, the other one of the electromagnetic bearing and the aerostatic bearing may serve as a standby bearing to perform the same function. For example, in the case of detecting the failure of the electromagnetic bearing, an external air source is controlled to be opened to perform corresponding actions instead of the electromagnetic bearing, so that the safety and the reliability of the bearing are improved.

The embodiment of the utility model provides an in, to being provided with electromagnetic bearing and aerostatic bearing's the condition simultaneously under, can include following embodiment:

turning on the fourth magnetic bearing; and/or starting an external gas source, and conveying gas to the fourth gap through the second static pressure gas inlet throttling hole;

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

Wherein, to the embodiment of opening fourth magnetic bearing and aerostatic bearing simultaneously, can further improve the utility model discloses radial bearing's of embodiment bearing capacity.

In the process, the fourth magnetic bearing is utilized to facilitate the real-time control, and the unbalanced mass of the rotating shaft or the factors of excessive deviation of the rotating shaft caused by the whirling motion of the rotating shaft and the like are actively balanced, so that the rotating shaft is fixed in a certain minimum range in the radial direction. In addition, in the acceleration process of the rotating shaft, the position (namely the linear velocity supersonic speed position) where the shock wave is generated can be accurately positioned, and the shock wave action is balanced by controlling the current magnitude, the current direction and the like of the fourth magnetic bearing to enable the fourth magnetic bearing to generate opposite force. And after the shock wave is stable, adjusting the control strategy of the fourth magnetic bearing again, and fixing the rotating shaft in a certain minimum range in a most energy-saving mode.

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

And secondly, for the traditional gas hybrid thrust bearing that adopts aerostatic bearing and gas dynamic pressure bearing to combine, the utility model discloses the mixed journal bearing of slot type gas magnetism has the fast advantage of response speed.

And thirdly, the gas hydrostatic bearing is added to form a groove type hybrid dynamic-static pressure-magnetic thrust bearing, under the condition that the electromagnetic bearing and the gas hydrostatic bearing are arranged at the same time, the bearing capacity of the bearing is further increased, the electromagnetic bearing and the gas hydrostatic bearing can be mutually standby, and under the condition that one of the two bearings is failed, fails or cannot meet the starting condition, the other bearing can be used as a standby bearing to play the same role. For example, in the case of detecting the failure of the electromagnetic bearing, the control system controls the aerostatic bearing to be opened to replace the electromagnetic bearing to perform corresponding actions, so that the safety and the reliability of the bearing are improved.

The above embodiments are only specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily think of changes or substitutions within the technical scope of the present invention, and all should be covered within the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.

Claims

1. A bearing for mounting on a rotating shaft, the bearing comprising:

2. The bearing of claim 1,

the radial sub-bearing comprises a first magnetic bearing sleeved on the rotating shaft, a first gap is formed between the first magnetic bearing and the rotating shaft, and a plurality of first magnetic components are arranged on the first magnetic bearing along the circumferential direction; the rotating shaft is movable in a radial direction of the rotating shaft by a magnetic force of the plurality of first magnetic members;

3. The bearing of claim 2,

the first magnetic bearing includes:

4. The bearing of claim 2,

the plurality of first magnetic components comprise a plurality of first permanent magnets circumferentially disposed on the first magnetic bearing;

5. The bearing of claim 2,

the first magnetic bearing is provided with a first dynamic pressure generating groove on the side wall facing the rotating shaft or the circumferential surface of the rotating shaft facing the first magnetic bearing.

6. The bearing of claim 2,

the radial sub-bearing further comprises a plurality of first sensors arranged at intervals along the circumferential direction of the first magnetic bearing, wherein the plurality of first sensors are any one or combination of the following:

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

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

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

7. The bearing of claim 6,

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

8. The bearing of claim 2,

the second magnetic bearing includes:

9. The bearing of claim 2,

the plurality of second magnetic components comprise a plurality of second permanent magnets circumferentially disposed on the second magnetic bearing;

10. The bearing of claim 2,

the third magnetic member includes a magnetic material provided on an end surface of the thrust disk facing the first stator and the second stator;

11. The bearing of claim 2,

the thrust disc may have end surfaces facing the first stator and the second stator, or end surfaces facing the thrust disc of the first stator and the second stator may have second dynamic pressure generating grooves.

12. The bearing of claim 11,

the second dynamic pressure generating grooves are arranged in a radial or concentric circle shape.

13. The bearing of claim 12,

the second dynamic pressure generating groove comprises a first spiral groove and a second spiral groove, the first spiral groove surrounds the second spiral groove, the spiral directions of the first spiral groove and the second spiral groove are opposite, and one end of the first spiral groove close to the second spiral groove is connected with or disconnected from one end of the second spiral groove close to the first spiral groove.

14. The bearing of claim 2,

the thrust sub-bearing is also provided with a second sensor, and the second sensor is any one or combination of more than one of the following sensors:

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

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

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

15. The bearing of claim 14,

the second sensor comprises a second sensor cover and a second sensor probe, the first end of the second sensor probe is connected with the second sensor cover, the second sensor cover is fixed on the second magnetic bearing, and a through hole for the second sensor probe to pass through is formed in the second magnetic bearing; the second end of the second sensor probe penetrates through the through hole in the second magnetic bearing and extends to the second gap, and the end part of the second end of the second sensor probe is flush with one side, close to the thrust disc, of the second magnetic bearing.

16. The bearing of claim 2,

the bearing shell is also provided with a static pressure air inlet throttling hole;

17. A rotor system, characterized in that,

the thrust bearing and a radial bearing adjacent to the thrust bearing are integrated to form a bearing as claimed in any one of claims 2 to 15.

18. The rotor system of claim 17,

19. The rotor system of claim 17,