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

A kind of bearing and rotor-support-foundation system

Technical field

The utility model relates to technical field of bearings more particularly to a kind of bearings and rotor-support-foundation system.

Background technique

Gas turbine mainly includes compressor, combustion chamber and the big component of turbine three.Air is compressed into after entering compressor The air of high temperature and pressure, then supplies combustion chamber and fuel is mixed and burned, and the high-temperature high-pressure fuel gas generated expands in turbine Acting.When rotor high-speed rotation, rotor will receive the power of radial direction or axial direction.Radial direction or axis occurs in order to limit shaft Upward movement needs to install transverse bearing and thrust bearing in rotor-support-foundation system.Traditional transverse bearing and thrust bearing be Contact bearing, with the raising of rotor speed, especially rotor speed per minute more than 40000 turns when, contact bearing by In there are biggish mechanical wears, the demand of working speed is had been unable to meet.

In existing rotor-support-foundation system, transverse bearing and thrust bearing are processed respectively and are installed respectively, in this way, leading to radial axle It holds with thrust bearing in processing or installation process it is difficult to ensure that the consistent requirement of concentricity.

Utility model content

The utility model provides a kind of bearing and rotor-support-foundation system, to solve in existing rotor-support-foundation system because of transverse bearing and thrust The problem that bearing is processed respectively, installs and cause the concentricity consistency of transverse bearing and thrust bearing lower.

In a first aspect, the utility model provides a kind of bearing, for being installed on shaft, the bearing includes：

Cartridge housing, the cartridge housing are hollow revolving body, and the cartridge housing is provided with the first accommodating chamber and the second accommodating chamber；

The sub- bearing of radial direction being set in first accommodating chamber, the sub- bearing of radial direction are arranged in the shaft, institute Stating has the first gap between radial sub- bearing and the shaft；

And it is set to the sub- bearing of thrust in second accommodating chamber, the sub- bearing of thrust includes thrust disc, and It is respectively arranged at the first stator and the second stator of the thrust disc two sides, the thrust disc is fixedly connected in the shaft, First stator and second stator are arranged in the shaft；In first stator and second stator, often There is the second gap between a stator and the thrust disc.

Optionally, the sub- bearing of the radial direction includes the first magnetic bearing being sheathed in the shaft, first magnetic bearing There is first gap between the shaft, it is circumferentially arranged on first magnetic bearing to have multiple first magnetic parts； The shaft can under the magneticaction of the multiple first magnetic part moving in the radial direction in the shaft；

In first stator and second stator, each stator includes the second magnetic bearing, on second magnetic bearing It is circumferentially arranged to have multiple second magnetic parts；It is provided with third magnetic part on the thrust disc, the thrust disc can be Under magneticaction between the multiple second magnetic part and the third magnetic part on the axial direction of the shaft It is mobile.

Optionally, first magnetic bearing includes：

First magnetic bearing seat, the first magnetic bearing cover for seat is set in the shaft, along week on the first magnetic bearing seat To multiple first holding tanks are provided with, the multiple first magnetic part is set in the multiple first holding tank, and described The magnetic pole of multiple first magnetic parts is towards the shaft；

And be sheathed on the bearing holder (housing, cover) between the first magnetic bearing seat and the shaft, the bearing holder (housing, cover) with described turn There is first gap, the bearing holder (housing, cover) and the first magnetic bearing seat cooperate, by the multiple first magnetic portion between axis Part is fixed on the first magnetic bearing seat.

Optionally, the multiple first magnetic part includes multiple first permanent magnets, and the multiple first permanent magnet is in institute It states circumferentially arranged on the first magnetic bearing；

Alternatively, the multiple first magnetic part includes multiple first electromagnet, the multiple first electromagnet is described Circumferentially arranged on first magnetic bearing, the first electromagnet of each of the multiple first electromagnet includes being set to described first The first magnetic core on magnetic bearing and the first coil being wound on first magnetic core.

Optionally, first magnetic bearing is towards the side wall of the shaft or the shaft towards first magnetic bearing Periphery is provided with the first dynamic pressure generation trough.

Optionally, the sub- bearing of the radial direction further includes passing along circumferentially spaced multiple the first of first magnetic bearing Sensor, the multiple first sensor are any one or more following combination：

For detecting the displacement sensor of the rotating shaft position；

For detecting the pressure sensor of the gas film pressure of first gap location；

For detecting the velocity sensor of the shaft revolving speed；

For detecting the acceleration transducer of the shaft rotary acceleration.

Optionally, in the multiple first sensor, each first sensor includes passing the first sensor lid and the first sensing The first end of device probe, the first sensor probe connects the first sensor lid, and the first sensor lid is fixed on On first magnetic bearing, first magnetic bearing be equipped with for for the first sensor probe across through-hole；It is described The second end of first sensor probe passes through the through-hole on first magnetic bearing, and extends to first gap, and described the The second end end of one sensor probe is concordant close to the side of the shaft with first magnetic bearing.

Optionally, second magnetic bearing includes：

Second magnetic bearing seat, the second magnetic bearing seat are oppositely arranged with the thrust disc, on the second magnetic bearing seat Circumferentially arranged to have multiple second holding tanks, the multiple second magnetic part is set in the multiple second holding tank, and Side where the magnetic pole towards the thrust disc of the multiple second magnetic part；

Pressure ring, the pressure ring be set to the second magnetic bearing seat close to the thrust disc side, the pressure ring with The second magnetic bearing seat cooperation, the multiple second magnetic part is fixed on the second magnetic bearing seat.

Optionally, the multiple second magnetic part includes multiple second permanent magnets, and the multiple second permanent magnet is in institute It states circumferentially arranged on the second magnetic bearing；

Alternatively, the multiple second magnetic part includes multiple second electromagnet, the multiple second electromagnet is described Circumferentially arranged on second magnetic bearing, the second electromagnet of each of the multiple second electromagnet includes being set to described second The second magnetic core on magnetic bearing and the second coil being wound on second magnetic core.

Optionally, the third magnetic part include be set to the thrust disc towards first stator and described Magnetic material on the end face of two stators；

Wherein, magnetic material distribution in a strip shape on the thrust disc, and multiple strip magnetic portions are formed, it is described more A strip magnetic portion is radially or circumferentially；

Alternatively, the magnetic material is in spot distribution on the thrust disc.

Optionally, the end face towards first stator and second stator of the thrust disc, or, described first is fixed The second dynamic pressure generation trough is provided on the end face towards the thrust disc of sub and described second stator.

Optionally, the second dynamic pressure generation trough is radially or concentric circles are arranged.

Optionally, the second dynamic pressure generation trough includes the first spiral groove and the second spiral groove, the first spiral grooved ring It is around in outside second helicla flute, the spiral of first helicla flute and second helicla flute is moved towards on the contrary, first spiral shell One end close to second helicla flute of spin slot is connect with one end close to first helicla flute of second helicla flute Or it disconnects.

Optionally, second sensor is additionally provided on the sub- bearing of the thrust, the second sensor is following any one Kind or a variety of combinations：

For detecting the displacement sensor of the thrust disc position；

For detecting the pressure sensor of the gas film pressure of second gap location；

For detecting the velocity sensor of the thrust disk rotating speed；

For detecting the acceleration transducer of the thrust disc rotary acceleration.

Optionally, the second sensor includes second sensor lid and second sensor probe, the second sensor The first end of probe connects the second sensor lid, and the second sensor lid is fixed on second magnetic bearing, described Second magnetic bearing be equipped with for for the second sensor probe across through-hole；The second end of the second sensor probe Through-hole on second magnetic bearing, and second gap is extended to, and the second end end of second sensor probe Portion is concordant close to the side of the thrust disc with second magnetic bearing.

Optionally, the cartridge housing is additionally provided with static pressure air inlet restriction hole；

Wherein, the one end in static pressure air inlet restriction hole connects external air source, and the other end is through the sub- bearing of the radial direction and institute It states the first gap to communicate, and is communicated through first stator and second stator with second gap, the static pressure air inlet Throttle orifice is used to external air source being delivered to first gap and second gap.

Second aspect, the utility model provide a kind of rotor-support-foundation system, which is characterized in that

Including shaft and the thrust bearing and at least two transverse bearings that are set in the shaft, the thrust bearing and At least two transverse bearing is non-contact type bearing；

The thrust bearing and the transverse bearing adjacent with the thrust bearing are integrated, are formed any in first aspect Bearing described in.

Optionally, the axis body of the shaft is structure as a whole, and the shaft is horizontally disposed or vertically arranged；

Motor, compressor and turbine are disposed in the shaft；

Wherein, the thrust bearing is set on the predeterminated position of the side of the close compressor of the turbine, institute Stating predeterminated position is that the center of gravity of the rotor-support-foundation system can be made to be located at two of lie farthest away at least two transverse bearing Position between transverse bearing.

It is non-that motor, compressor, turbine and two transverse bearings, described two transverse bearings are provided in the shaft Contact bearing；

The rotor-support-foundation system further includes the first casing and the second casing, and first casing is connect with second casing；

Wherein, the motor, the thrust bearing and described two transverse bearings are all set in first casing, institute It states compressor and the turbine is all set in second casing, the impeller of the impeller of the compressor and the turbine is in institute It states in the second casing mutually by setting.

In the utility model, by the way that radial sub- bearing and the sub- bearing of thrust are integrated in a cartridge housing, structure letter Single, integrated level height, and it is easily manufactured and installed, it can effectively ensure that radial sub- bearing and the sub- bearing of thrust in processing and installation The consistent requirement of concentricity.In addition, the utility model is due to being provided with gap in radial sub- bearing and the sub- bearing of thrust, this The bearing of utility model is non-contact type bearing, can satisfy the demand of rotor high-speed rotation.

Detailed description of the invention

In order to illustrate more clearly of the technical solution of the utility model embodiment, the utility model embodiment will be retouched below Attached drawing needed in stating is briefly described, it should be apparent that, the accompanying drawings in the following description is only the utility model Some embodiments for those of ordinary skill in the art without any creative labor, can be with root Other attached drawings are obtained according to these attached drawings.

Fig. 1 is a kind of cross-sectional view for bearing that embodiment one provides；

Fig. 2 be in Fig. 1 A-A to cross-sectional view；

Fig. 3 is the cross-sectional view of B-B direction in Fig. 1；

Fig. 4 is the structural schematic diagram of the first magnetic bearing seat in the bearing of the offer of embodiment one；

Fig. 5 is the structural schematic diagram of the second magnetic bearing seat in the bearing of the offer of embodiment one；

Fig. 6 be embodiment one provide bearing in be arranged on bearing holder (housing, cover) the first dynamic pressure generation trough structural schematic diagram it One；

Fig. 7 be embodiment one provide bearing in be arranged on bearing holder (housing, cover) the first dynamic pressure generation trough structural schematic diagram it Two；

Fig. 8 is that the structural schematic diagram of the first dynamic pressure generation trough is arranged in shaft in bearing that embodiment one provides；

Fig. 9 be embodiment one provide bearing in be arranged on thrust disc the second dynamic pressure generation trough structural schematic diagram it One；

Figure 10 be embodiment one provide bearing in be arranged on thrust disc the second dynamic pressure generation trough structural schematic diagram it Two；

Figure 11 is that one of the structural schematic diagram of the second dynamic pressure generation trough is arranged on pressure ring in bearing that embodiment one provides；

Figure 12 is that the second structural representation of the second dynamic pressure generation trough is arranged on pressure ring in bearing that embodiment one provides；

Figure 13 is a kind of structural schematic diagram for rotor-support-foundation system that embodiment two provides；

Figure 14 is a kind of structural schematic diagram for rotor-support-foundation system that embodiment three provides；

Figure 15 is a kind of structural schematic diagram for rotor-support-foundation system that example IV provides；

Figure 16 is the structural schematic diagram for another rotor-support-foundation system that example IV provides；

Figure 17 is a kind of structural schematic diagram that locking device is arranged in rotor-support-foundation system that embodiment five provides；

Figure 18 is another structural schematic diagram that locking device is arranged in rotor-support-foundation system that embodiment five provides；

Figure 19 be in Figure 18 C-C to structural schematic diagram；

Figure 20 is the structural schematic diagram that anti-abrasive coatings are coated in shaft that embodiment six provides；

Figure 21 is a kind of flow diagram of the control method for bearing that embodiment seven provides；

Figure 22 is the flow diagram of the control method for another bearing that embodiment seven provides；

Figure 23 is a kind of cross-sectional view for paillon formula gas magnetic hybrid radial bearing that embodiment eight provides；

Figure 24 is the external view for the paillon formula gas magnetic hybrid radial bearing that embodiment eight provides；

Figure 25 is the structural schematic diagram of third magnetic bearing seat in the paillon formula gas magnetic hybrid radial bearing of the offer of embodiment eight；

Figure 26 is that strip magnetism is distributed in the paillon formula gas magnetic hybrid radial bearing of the offer of embodiment eight on the 4th paillon The structural schematic diagram of material；

Figure 27 is the structural schematic diagram that the 4th paillon shown in Figure 26 is unfolded；

Figure 28 is that dotted magnetism is distributed on the 4th paillon in the paillon formula gas magnetic hybrid radial bearing of the offer of embodiment eight The structural schematic diagram of material；

Figure 29 is the structural schematic diagram that the 4th paillon shown in Figure 28 is unfolded；

Figure 30 is the enlarged diagram of part A in Figure 23；

Figure 31 is a kind of half sectional view for slot type gas magnetic hybrid radial bearing that embodiment nine provides；

Figure 32 is the half sectional view for another slot type gas magnetic hybrid radial bearing that embodiment nine provides；

Figure 33 is a kind of external view for slot type gas magnetic hybrid radial bearing that embodiment nine provides；

Figure 34 is the structural schematic diagram of the 4th magnetic bearing in the slot type gas magnetic hybrid radial bearing of the offer of embodiment nine；

Figure 35 is the structural schematic diagram of the 4th magnetic bearing seat in the slot type gas magnetic hybrid radial bearing of the offer of embodiment nine；

Figure 36 is that third dynamic pressure is arranged on second bearing set in the slot type gas magnetic hybrid radial bearing of the offer of embodiment nine One of structural schematic diagram of generation trough；

Figure 37 is that third dynamic pressure is arranged on second bearing set in the slot type gas magnetic hybrid radial bearing of the offer of embodiment nine The second structural representation of generation trough；

Figure 38 is that third dynamic pressure generation trough is arranged in the slot type gas magnetic hybrid radial bearing of the offer of embodiment nine in shaft Structural schematic diagram.

Specific embodiment

The following will be combined with the drawings in the embodiments of the present invention, carries out the technical scheme in the embodiment of the utility model It clearly and completely describes, it is clear that the embodiments are a part of the embodiments of the present invention, rather than whole implementation Example.Based on the embodiments of the present invention, those of ordinary skill in the art are obtained without creative efforts The every other embodiment taken, fall within the protection scope of the utility model.

As shown in Figures 1 to 12, bearing 1000, for being installed on shaft 100, bearing 1000 includes：

Cartridge housing 1001, cartridge housing 1001 are hollow revolving body, and cartridge housing 1001, which is provided with the first accommodating chamber and second, to be held Receive chamber；

The sub- bearing 102 of the radial direction being set in the first accommodating chamber, radial sub- bearing 102 are arranged in shaft 100, radial son There is the first gap 104 between bearing 102 and shaft 100；

And the sub- bearing 103 of thrust being set in the second accommodating chamber, the sub- bearing 103 of thrust include thrust disc 1031, with And it is respectively arranged at the first stator 1032 and the second stator 1033 of 1031 two sides of thrust disc, thrust disc 1031, which is fixedly connected on, to be turned On axis 100, the first stator 1032 and the second stator 1033 are arranged in shaft 100；First stator 1032 and the second stator In 1033, there is the second gap 105 between each stator and thrust disc 1031.

In the utility model embodiment, radial sub- bearing 102 and the sub- bearing 103 of thrust are integrated in a cartridge housing 1001 It is interior, it is easily manufactured and installed, have the characteristics that structure is simple, integrated level is high, can effectively ensure that radial direction in processing and installation The consistent requirement of concentricity of sub- bearing 102 and the sub- bearing 103 of thrust.In addition, due to being provided with first in radial sub- bearing 102 Gap 104 is provided with the second gap 105 in the sub- bearing 103 of thrust, so that the bearing of the utility model is non-contact type bearing, It can satisfy the demand of rotor high-speed rotation.

Wherein, the material of cartridge housing 1001 can be non-magnetic material, preferably duralumin material.

Wherein, the first stator 1032 can be integrally formed with cartridge housing 1001, and the second stator 1033 can with cartridge housing 1001 To be to be detachably connected.

When the bearing of the utility model embodiment is applied to gas turbine or gas turbine power generation Unit erriger, bearing Shell 1001 can be connected by the shell of connector and gas turbine.

In the preferred embodiment in the utility model, radial sub- bearing 102 includes the first magnetic bearing being sheathed in shaft 100 1021, there is the first gap 104 between the first magnetic bearing 1021 and shaft 100, it is circumferentially arranged on the first magnetic bearing 1021 to have Multiple first magnetic parts 10211；Shaft 100 can be under the magneticaction of multiple first magnetic parts 10211 in shaft 100 Move in the radial direction；In first stator 1032 and the second stator 1033, each stator include the second magnetic bearing 1034, second It is circumferentially arranged on magnetic bearing 1034 to have multiple second magnetic parts 10341；Third magnetic part is provided on thrust disc 1031, Thrust disc 1031 can be under the magneticaction between multiple second magnetic parts 10341 and third magnetic part in shaft 100 Axial direction on move.

In the preferred embodiment in the utility model, by the way that the first gap 104 and the first magnetic axis is arranged in radial sub- bearing 102 1021 are held, so that the sub- bearing 102 of the radial direction be made to form gas, the sub- bearing 102 of magnetic hybrid radial；By in the sub- bearing 103 of thrust The second gap 105 of middle setting and the second magnetic bearing 1034, so that the sub- bearing 103 of the thrust be made to form gas, the magnetic mixing sub- axis of thrust Hold 103.

When work, radial sub- bearing 102 and the sub- bearing 103 of thrust can cooperate, and make shaft 100 radial and axial It keeps stablizing on direction；In addition, the gas bearing in radial sub- bearing 102 and the sub- bearing 103 of thrust also can with magnetic bearing Cooperate, to shaft 100 carry out in time, efficiently control.

As it can be seen that the bearing of the preferred embodiment in the utility model can guarantee shaft 100, especially under the state of running at high speed Dynamic property and stability resist disturbed kinetic force strong, and then improve the bearing capacity of bearing.The axis of the utility model embodiment Hold the demand that can satisfy high-revolving gas turbine or gas turbine power generation Unit erriger etc..

Optionally, the first magnetic bearing 1021, which can be, is removably mounted in the first accommodating chamber.

Further, bearing further includes end cap 106, and end cap 106 is set to close first accommodating chamber of cartridge housing 1001 End, end cap 106 are abutted with the first magnetic bearing 1021, for the first magnetic bearing 1021 to be fixed in the first accommodating chamber.Wherein, The material of end cap 106 can be non-magnetic material, preferably duralumin material.

Optionally, cartridge housing 1001 is additionally provided with static pressure air inlet restriction hole 107；Wherein, the one of static pressure air inlet restriction hole 107 End connection external air source, the other end are communicated through radial sub- bearing 102 with the first gap 104, and through the first stator 1032 and second Stator 1033 is communicated with the second gap 105, and static pressure air inlet restriction hole 107 is used to external air source being delivered to 104 He of the first gap Second gap 105.

In the utility model embodiment, by the way that above-mentioned static pressure air inlet restriction hole 107 is arranged, to make radial sub- bearing 102 It include aerostatic bearing with the sub- bearing 103 of thrust, so that radial sub- bearing 102 may be constructed gas dynamic and static pressure-magnetic mixing Radial sub- bearing 102, the sub- bearing 103 of thrust may be constructed gas dynamic and static pressure-magnetic mixing sub- bearing 103 of thrust.Wherein, static pressure into The circulation diameter of moral discharge orifice 107 can be adjusted according to actual conditions such as tolerance demands.

Due to being provided with magnetic bearing and aerostatic bearing simultaneously, the bearing capacity of bearing 1000 can be made further to increase. In addition, magnetic bearing and aerostatic bearing can be mutually spare, wherein side's failure, fail or be unable to satisfy unlocking condition In the case where, another party can be used as replacement bearing and serve the same role.For example, leading to the case where detecting magnetic bearing failure Control aerostatic bearing is crossed to open to substitute magnetic bearing and execute corresponding movement, thus improve bearing 1000 safety and can By property.

In order to better understand in the bearing of the utility model embodiment every sub- bearing specific structure, it is right separately below Radial sub- bearing 102 and the sub- bearing 103 of thrust are described further.

Wherein, for radial sub- bearing 102：

As an implementation, the first magnetic bearing 1021 includes：

First magnetic bearing seat 10212, the first magnetic bearing seat 10212 are sheathed in shaft 100, the first magnetic bearing seat 10212 Above circumferentially arranged to have multiple first holding tanks 10213, multiple first magnetic parts 10211 are set to multiple first holding tanks In 10213, and the magnetic pole of multiple first magnetic parts 10211 is towards shaft 100；

And be sheathed on the bearing holder (housing, cover) 10212 between the first magnetic bearing seat 10212 and shaft 100, bearing holder (housing, cover) 10212 with There is the first gap 104, bearing holder (housing, cover) 10212 and the first magnetic bearing seat 10212 cooperate, magnetic by multiple first between shaft 100 Component 10211 is fixed on the first magnetic bearing seat 10212.

In the embodiment, by the way that bearing holder (housing, cover) 10212 is arranged, magnetic core 1011 and coil 1012 and the first magnetic can be closed Gap between bearing block 10212, to form stable, uniform gas film pressure between bearing holder (housing, cover) 10212 and shaft 100. In addition, can be conveniently adjusted and control the size in the first gap 104 by the bearing holder (housing, cover) 10212 that different radial thickness are arranged.

Wherein, the width in the first gap 104 between bearing holder (housing, cover) 10212 and shaft 100 can be 5 μm to 12 μm, preferably 8 μm to 10 μm.

It should be noted that when shaft 100 is not opened, shaft 100 and the concentric setting of bearing holder (housing, cover) 10212, shaft 100 After unlatching, any side in the axle center of the axis deviation bearing holder (housing, cover) 10212 of shaft 100, and eccentricity epsilon is 0.3 to 0.5, to protect The first wedge-shaped gap 104 is capable of forming between card bearing holder (housing, cover) 10212 and shaft 100.When shaft 100 rotates, gas is pressed Enter the first gap 104, to generate pressure to support load.Wherein, eccentricity epsilon=e/ (R-r), wherein e is shaft 100 Axle center to the distance between the axle center of bearing holder (housing, cover) 10212, R are the internal diameter of bearing holder (housing, cover) 10212, and r is the internal diameter of shaft 100, (R- It r) is the width of bearing clearance.

Wherein, since silicon steel sheet or silicon steel sheet have the physical characteristics such as magnetic conductivity is high, eddy-current loss is low, the utility model In preferred embodiment, the first magnetic bearing seat 10212 is overrided to form by several silicon steel sheets or silicon steel sheet.First holding tank 10213 Quantity can be but be not limited to six or eight, the circumferential direction along the first magnetic bearing seat 10212 is uniformly arranged.In such manner, it is possible to Keep the magnetic force of the first magnetic bearing 1021 more uniform, stable.It should be noted that multiple first magnetic parts 10211 can be with It is set on the first magnetic bearing seat 10212 using other modes, to this without limiting.The material of bearing holder (housing, cover) 10212 can be Non-magnetic material, preferably duralumin material.

As an implementation, multiple first magnetic parts 10211 include multiple first permanent magnets, multiple first permanent magnetism Body is circumferentially arranged on the first magnetic bearing 1021；Alternatively, multiple first magnetic parts 10211 include multiple first electromagnet, Multiple first electromagnet are circumferentially arranged on the first magnetic bearing 1021, the first electromagnet packet of each of multiple first electromagnet Include the first magnetic core being set on the first magnetic bearing 1021 and the first coil being wound on the first magnetic core.

In the embodiment, when radial sub- bearing 102 only needs the first magnetic part 10211 to provide magnetic force without magnetic control When, the preferred permanent magnet of the first magnetic part 10211；When radial sub- bearing 102 needs the first magnetic part 10211 to provide magnetic simultaneously When power and magnetic control, the preferred electromagnet of the first magnetic part 10211.

When the first magnetic part 10211 is electromagnet, electric current is passed through toward first coil, it can generate the first magnetic core Magnetic force.It is passed through the of different sizes of electric current toward first coil, the magnetic force size that the first magnetic core generates is also different；It is passed through toward first coil Sense of current is different, and the magnetic pole of the first magnetic core is also different.

Wherein, since silicon steel sheet or silicon steel sheet have the physical characteristics such as magnetic conductivity is high, eddy-current loss is low, the utility model In preferred embodiment, the first magnetic core can be overrided to form by several silicon steel sheets or silicon steel sheet.

As an implementation, side wall and/or shaft 100 towards first of first magnetic bearing 1021 towards shaft 100 The periphery of magnetic bearing 1021 is provided with the first dynamic pressure generation trough 1022.

In the embodiment, when shaft 100 rotates, the flowing gas for being present in the first gap 104 is pressed into first and moves It presses in generation trough 1022, to generate pressure, so that shaft 100 is floated, to realize that shaft 100 is radially non-contactly protected It holds.Wherein, the first dynamic pressure generation trough 1022 generate pressure size with the angle of the first dynamic pressure generation trough 1022, groove width, flute length, Groove depth, the difference of slot number and flatness and change.In addition, the first dynamic pressure generation trough 1022 generates the size of pressure also and shaft 100 rotation speed and the first gap 104 are related.It can be according to actual condition to the parameter of the first dynamic pressure generation trough 1022 It is designed.First dynamic pressure generation trough 1022 can be formed in the first magnetic bearing by modes such as forging, rolling, etching or punching presses 1021 or shaft 100 on.

In conjunction with aforementioned embodiments, in the embodiment, the first dynamic pressure generation trough can be set on bearing holder (housing, cover) 10212 1022, for the processing convenient for the first dynamic pressure generation trough 1022, bearing holder (housing, cover) 10212 can be made of stainless steel material.Specifically, The middle section of the periphery of respective shaft bearing sleeve 10212 in shaft 100 can be set in one dynamic pressure generation trough 1022, can also set It is set to the two sides for being symmetrically distributed in middle section, the first dynamic pressure of mutually independent two parts generation trough 1022；First dynamic pressure occurs The middle section of 10212 inner sidewall of bearing holder (housing, cover) can also be arranged in slot 1022, may be set to be and be symmetrically distributed in bearing holder (housing, cover) 10212 inner sidewall both ends, the first dynamic pressure of mutually independent two parts generation trough 1022.

Optionally, the first dynamic pressure generation trough 1022 is arranged in matrix.In this way, being conducive to that air film is made to be more evenly distributed in In one gap 104.

Further, the first dynamic pressure generation trough 1022 is continuous or spaced V-shaped groove.In such manner, it is possible in shaft 100 In the case where rotating in the forward direction or reversely rotating, shaft 100 can be kept in a non-contact manner in the desired manner, to make shaft 100 have the advantages that high load capacity and stability are good.First dynamic pressure generation trough 1022 can also be set in addition to being set as V-shaped groove It is set to man type chute or other shapes of slot.

As an implementation, radial sub- bearing 102 further includes along the circumferentially spaced of the first magnetic bearing 1021 Multiple first sensor (not shown)s, wherein the sensor probe of each first sensor is set in the first gap 104.

In such manner, it is possible to the gas film pressure etc. at the parameter at the first gap of real-time detection 104, such as the first gap 104.This Sample, the first magnetic bearing 1021 can carry out active control, and energy to radial sub- bearing 102 according to the testing result of first sensor Control is enough set to reach higher precision.

Optionally, in multiple first sensors, each first sensor includes passing the first sensor lid and first sensor spy The first end of head, first sensor probe connects first sensor lid, and first sensor lid is fixed on the first magnetic bearing 1021, First magnetic bearing 1021 be equipped with for for first sensor probe across through-hole；The second end of first sensor probe passes through Through-hole on first magnetic bearing 1021, and the first gap 104 is extended to, and the second end end of first sensor probe and the first magnetic The side of the close shaft 100 of bearing 1021 is concordant.

In such manner, it is possible to be set to first sensor more stably on the first magnetic bearing 1021.In addition, by sensor probe Second end end it is concordant with the side of close shaft 100 of the first magnetic bearing 1021, can be avoided sensor probe by turn Axis 100 touches, to be conducive to protect sensor probe.

Optionally, in multiple first sensors, each first sensor is respectively arranged at two adjacent the first magnetic portions Between part 10211.For example, the quantity of first sensor may be when the quantity of the first magnetic part 10211 is eight Eight, each first sensor is respectively arranged between two adjacent the first magnetic parts 10211, and each first sensor is excellent Choosing is set to the middle part of the first magnetic bearing 1021.

Optionally, multiple first sensors are any one or more following combination：

For detecting the displacement sensor of 100 position of shaft；

For detecting the pressure sensor of the gas film pressure at the first gap 104；

For detecting the velocity sensor of 100 revolving speed of shaft；

For detecting the acceleration transducer of 100 rotary acceleration of shaft.

Wherein, bearing 103 sub- for thrust：

As an implementation, the second magnetic bearing 1034 includes：

Second magnetic bearing seat 10342, the second magnetic bearing seat 10342 are oppositely arranged with thrust disc 1031, the second magnetic bearing seat Circumferentially arranged on 10342 to have multiple second holding tanks 10343, multiple second magnetic parts 10341, which are set to multiple second, to be held It receives in slot 10343, and the side where the magnetic pole of multiple second magnetic parts 10341 towards thrust disc 1031；

Pressure ring 10344, pressure ring 10344 are set to the side of the close thrust disc 1031 of the second magnetic bearing seat 10342, pressure ring 10344 and second magnetic bearing seat 10342 cooperate, multiple second magnetic parts 10341 are fixed on the second magnetic bearing seat 10342 On.

Wherein, since silicon steel sheet or silicon steel sheet have the physical characteristics such as magnetic conductivity is high, eddy-current loss is low, the utility model In preferred embodiment, the second magnetic bearing seat 10342 is overrided to form by several silicon steel sheets or silicon steel sheet.Second holding tank 10343 Quantity can be but be not limited to six or eight, the circumferential direction along the second magnetic bearing seat 10342 is uniformly arranged.In such manner, it is possible to Keep the magnetic force between the second magnetic bearing 1034 and thrust disc 1031 more uniform, stable.It should be noted that multiple second is magnetic Component 10341 can also be set on the second magnetic bearing seat 10342 using other modes, to this without limiting.Pressure ring 10344 Material can be non-magnetic material, preferably duralumin material.

The structure of the corresponding embodiment, the air inlet path in static pressure air inlet restriction hole 107 divide two-way to distinguish in cartridge housing 1001 It is connected to the annular gas runner of the annular gas runner of the first stator 1032 and the second stator 1033, the first stator 1032 and Second gap of the static pressure air inlet path one end of two stators 1033 across pressure ring 10344 and thrust disc 1031 and two stators 105 connections, the other end connect with the annular gas runner of the annular gas runner of the first stator 1032 and the second stator 1033 respectively It is logical.

As an implementation, multiple second magnetic parts 10341 include multiple second permanent magnets, multiple second permanent magnetism Body is circumferentially arranged on the second magnetic bearing 1034；

Alternatively, multiple second magnetic parts 10341 include multiple second electromagnet, multiple second electromagnet are in the second magnetic axis Hold it is circumferentially arranged on 1034, the second electromagnet of each of multiple second electromagnet include be set to the second magnetic bearing 1034 On the second magnetic core and the second coil for being wound on the second magnetic core.

In the utility model embodiment, when the sub- bearing 103 of thrust only needs the second magnetic part 10341 to provide magnetic force and nothing When needing magnetic control, the preferred permanent magnet of the second magnetic part 10341；When the sub- bearing 103 of thrust needs the second magnetic part 10341 simultaneously When magnetic force and magnetic control are provided, the preferred electromagnet of the second magnetic part 10341.

When the second magnetic part 10341 is electromagnet, electric current is passed through toward the second coil, it can generate the second magnetic core Magnetic force.It is passed through the of different sizes of electric current toward the second coil, the magnetic force size that the second magnetic core generates is also different；It is passed through toward the second coil Sense of current is different, and the magnetic pole of the second magnetic core is also different.

Wherein, since silicon steel sheet or silicon steel sheet have the physical characteristics such as magnetic conductivity is high, eddy-current loss is low, the utility model In preferred embodiment, the second magnetic core is overrided to form by several silicon steel sheets or silicon steel sheet.

As an implementation, third magnetic part include be set to thrust disc 1031 towards 1032 He of the first stator Magnetic material (not shown) on the end face of second stator 1033；

Wherein, magnetic material distribution in a strip shape on thrust disc 1031, and multiple strip magnetic portions are formed, multiple strip magnetic Property portion is radially or circumferentially；

Alternatively, magnetic material is in spot distribution on thrust disc 1031.

In the embodiment, make magnetic material distribution in a strip shape or spot distribution on thrust disc 1031, it can will be magnetic The magnetic force generated between material and the second magnetic part 10341 is controlled in reasonable range.

As an implementation, the end face towards the first stator 1032 and the second stator 1033 of thrust disc 1031, and/ Or, being provided with the second dynamic pressure generation trough on the end face towards thrust disc 1031 of the first stator 1032 and the second stator 1033 1035。

In the utility model embodiment, when thrust disc 1031 rotates, the flowing gas for being present in the second gap 105 is pressed Enter in the second dynamic pressure generation trough 1035, so that pressure is generated, to realize that thrust disc 1031 is in axial direction non-contactly kept. Wherein, the second dynamic pressure generation trough 1035 generates the size of pressure with the angle, groove width, flute length, slot of the second dynamic pressure generation trough 1035 The difference of deep, slot number and flatness and change.In addition, the second dynamic pressure generation trough 1035 generates the size of pressure also and thrust disc 1031 rotation speed and the second gap 105 are related.It can be according to actual condition to the parameter of the second dynamic pressure generation trough 1035 It is designed.Second dynamic pressure generation trough 1035 can be formed in the first stator by modes such as forging, rolling, etching or punching presses 1032 and second on stator 1033, alternatively, the second dynamic pressure generation trough 1035 can pass through the side such as forging, rolling, etching or punching press Formula is formed on thrust disc 1031.

In conjunction with aforementioned embodiments, in the embodiment, the second dynamic pressure generation trough can be set on pressure ring 10344 1035, for the processing convenient for the second dynamic pressure generation trough 1035, pressure ring 10344 can be made of stainless steel material.

Optionally, the second dynamic pressure generation trough 1035 is radially or concentric circles are arranged.In this way, being conducive to keep air film more equal It is distributed in the second gap 105 evenly.

Optionally, the second dynamic pressure generation trough 1035 includes the first helicla flute 10351 and the second helicla flute 10352, the first spiral shell Spin slot 10351 is surrounded on outside the second helicla flute 10352, and the spiral of the first helicla flute 10351 and the second helicla flute 10352 moves towards phase Instead, one end close to the second helicla flute 10352 of the first helicla flute 10351 is with the second helicla flute 10352 close to the first spiral One end of slot 10351 connects or disconnects.

Wherein, the distance in one end to the axle center of shaft 100 close to the second helicla flute 10352 of the first helicla flute 10351 Equal to the first helicla flute 10351 close to one end of the second helicla flute 10352 to the first stator 1032 or the second stator 1033 or The distance of the neighboring of thrust disc 1031.Alternatively, one end close to the first helicla flute 10351 of the second helicla flute 10352 is extremely The distance in the axle center of shaft 100 is equal to one end close to the first helicla flute 10351 of the second helicla flute 10352 to the first stator 1032 or second stator 1033 or thrust disc 1031 neighboring distance.

In such manner, it is possible to which thrust disc 1031 can be with desired in the case where shaft 100 is rotated in the forward direction or reversely rotated Mode is kept in a non-contact manner, so that shaft 100 be made to have the advantages that high load capacity and stability are good.

As an implementation, second sensor (not shown) is additionally provided on the sub- bearing 103 of thrust, second passes The sensor probe of sensor is set in the second gap 105.

In such manner, it is possible to the gas film pressure etc. at the parameter at the second gap of real-time detection 105, such as the second gap 105.This Sample, the second magnetic bearing 1034 can carry out active control, and energy to the sub- bearing of thrust 103 according to the testing result of second sensor Control is enough set to reach higher precision.

Optionally, second sensor includes second sensor lid and second sensor probe, and the of second sensor probe One end connects second sensor lid, and second sensor lid is fixed on the second magnetic bearing 1034, and the second magnetic bearing 1034 is equipped with For for second sensor probe across through-hole；The second end of second sensor probe passes through logical on the second magnetic bearing 1034 Hole, and the second gap 105 is extended to, and the close thrust disc of the second end end of second sensor probe and the second magnetic bearing 1034 1031 side is concordant.

In such manner, it is possible to be set to second sensor more stably on the second magnetic bearing 1034.In addition, by second sensor The second end end of probe is concordant with the side of close thrust disc 1031 of the second magnetic bearing 1034, can be avoided second sensor Probe is touched by thrust disc 1031, to be conducive to protect second sensor probe.

Optionally, second sensor is set between two adjacent the second magnetic parts 10341.

Wherein, at least one second sensor should all be set on each stator, is preferably provided with a second sensor, it should Second sensor is preferably provided between two neighboring second magnetic part 10341.

Optionally, second sensor is any one or more following combination：

For detecting the displacement sensor of 1031 position of thrust disc；

For detecting the pressure sensor of the gas film pressure at the second gap 105；

For detecting the velocity sensor of 1031 revolving speed of thrust disc；

For detecting the acceleration transducer of 1031 rotary acceleration of thrust disc.

Embodiment two

The utility model embodiment provides a kind of rotor-support-foundation system, including：

The axis body of shaft, the shaft is structure as a whole, and the shaft is horizontally disposed；

Motor, compressor and the turbine being set in turn in the shaft；

And it is set to thrust bearing and at least two transverse bearings in the shaft, the thrust bearing and described At least two transverse bearings are non-contact type bearing；

In the utility model embodiment, the thrust bearing and the transverse bearing adjacent with the thrust bearing integrated one Body forms bearing provided herein.

In the utility model embodiment, thrust bearing is the bearing moved in the axial direction for limiting shaft, radial Bearing is the bearing moved in radial directions for limiting shaft.

With the raising of rotor speed, common bearing has been unable to satisfy the needs of high revolving speed rotor.Therefore, this is practical In new embodiment, in order to adapt to the growth requirement of rotor high-speed rotation, thrust bearing and transverse bearing can be connect using non- Touch bearing.

In the utility model embodiment, the axis body of shaft is structure as a whole, it can be understood as, the axis body of shaft is one whole Axis, alternatively, the axis body of shaft is rigidly connected by multiple shaft parts.It is each in shaft since the axis body of shaft is structure as a whole The intensity for locating axis body is with uniformity, this makes setting position of the thrust bearing in shaft unrestricted.

Further, in order to make entire rotor-support-foundation system also be able to maintain stable structure, entire rotor-support-foundation system when rotating at high speed Center of gravity should be located at above-mentioned at least two transverse bearing in lie farthest away two transverse bearings between.In this way, entire rotor system System forms spindle structure, is different from traditional cantilever structure, the utility model embodiment improves entire rotor-support-foundation system Stability.Since thrust bearing is unrestricted in the setting position of shaft, it, can basis in the utility model embodiment The setting quantity of the transverse bearing of above-mentioned at least two transverse bearing, the setting position of each transverse bearing and entire rotor system The parameters such as quality (quality including thrust bearing itself) of each component carry out neatly the setting position of thrust bearing in system Adjustment, so that between entirely the center of gravity of rotor-support-foundation system is located between two transverse bearings of lie farthest away, it is preferred that entire rotor The center of gravity of system is located on compressor.

In the utility model embodiment, shaft is horizontally disposed, accordingly, it is to be understood that ground, the utility model embodiment turns Subsystem is horizontal rotor system, can be adapted for needing the horizontal unit using horizontal rotor system, such as Horizontal gas Turbine generator group.

As shown in figure 13, the utility model embodiment provides a kind of rotor-support-foundation system, including shaft 100 and thrust bearing 500, The axis body of shaft 100 is structure as a whole, and shaft 100 is horizontally disposed；

Motor 200, compressor 300 and turbine 400 are disposed in shaft 100；

The first transverse bearing 600 and the second transverse bearing 700, the first transverse bearing 600 and second are additionally provided in shaft Transverse bearing 700 is non-contact type bearing, wherein the first transverse bearing 600 and thrust bearing 500 are integrated, form collection Accepted way of doing sth bearing 10000；

First transverse bearing 600 is set to the side of the separate compressor 300 of motor 200, the setting of the second transverse bearing 700 Between compressor 300 and turbine 400, thrust bearing 500 is set between the first transverse bearing 600 and motor 200.

Currently, non-contact type bearing generally comprises electromagnetic bearing and air bearing.However, electromagnetic bearing is in long-term open The problems such as there are energy consumption is too big and fever；And air bearing can generate sharp when linear resonance surface velocity is near or above velocity of sound Wave so as to cause bearing unstability, or even generates the catastrophic effects such as bar resets.

Accordingly, it is considered to gas turbine or the high-revolving growth requirement of Gas Turbine Generating Units be arrived, in order to improve radial direction The working performance of bearing, in the utility model embodiment, the first transverse bearing 600 can use gas magnetic hybrid radial bearing or gas Body hybrid transverse bearing.Second transverse bearing 700 is due to close to turbine 400, it is contemplated that the magnetic part in magnetic bearing It can not be resistant to the high temperature that turbine 400 transmits, the second transverse bearing 700 can use gas hybrid transverse bearing.

As another embodiment, the second transverse bearing 700 can also use gas magnetic hybrid radial bearing, which Under, the magnetic part of the second transverse bearing 700 is set to the region of the separate turbine 400 on the second transverse bearing 700.Namely It says, the region of the close turbine 400 on the second transverse bearing 700 is not provided with magnetic part.

For the magnetic part on the second transverse bearing 700 of protection, the second radial axle can be radiated to by reducing turbine 400 The mode for holding the thermal energy on 700 is realized.Specifically, on turbine 400 close to the second transverse bearing 700 side be provided with it is heat-insulated Layer (not shown).Here, the material of thermal insulation layer can be aeroge or the good other materials of heat-proof quality.

In the utility model embodiment, compressor 300 can be centrifugal compressor 300, and 400 turbine of turbine can be centrifugation Formula turbine；Motor 200 can be Hydrodynamic bearing electric machine, and the position of the bearing of the corresponding motor 200 of shaft 100 can be set first Dynamic pressure generation trough 201；Motor 200 can also be starting-generating integrated motor, in this way, motor 200 can be in rotor-support-foundation system starting It is used as motor, to drive rotor-support-foundation system to rotate；After rotor-support-foundation system starting, motor 200, which can be used as generator, to be made With to realize that rotor-support-foundation system driven generator generates electricity.

Thrust bearing and transverse bearing in the rotor-support-foundation system of the utility model embodiment can also use other setting sides Formula, due to impossible to exhaust, the utility model embodiment no longer illustrates one by one.

Embodiment three

The axis body of shaft, the shaft is structure as a whole, and the shaft is vertically arranged；

Motor, compressor and the turbine being set in turn in the shaft；

With the raising of rotor speed, common bearing has been unable to satisfy the needs of high revolving speed rotor.Therefore, this is practical In new embodiment, in order to adapt to the growth requirement of rotor high-speed rotation, transverse bearing can use non-contact type bearing.

In the utility model embodiment, shaft is vertically arranged, accordingly, it is to be understood that ground, the utility model embodiment turns Subsystem is vertical rotor system, can be adapted for needing the vertical unit using vertical rotor system, such as Verticle gas Turbine generator group.

Since thrust bearing and transverse bearing are all made of non-contact type bearing, enable rotor-support-foundation system is vertical to be arranged.This The center of gravity of sample, rotor-support-foundation system is in axle center, will not generate quiet flexure, and the torque that gravity generates on axis is zero, can be disappeared Except gravity has an impact the rotation of rotor-support-foundation system, so as to improve the stability of rotor-support-foundation system.Simultaneously as rotor-support-foundation system The center of gravity of vertical setting, all components is downward, can be avoided cantilever axis structure institute caused by being horizontally disposed with because of rotor-support-foundation system The problem of bringing.

As shown in figure 14, the utility model embodiment provides a kind of rotor-support-foundation system, including shaft 100 and thrust bearing 500, The axis body of shaft 100 is structure as a whole, and shaft 100 is vertically arranged；

Motor 200, compressor 300 and turbine 400 are disposed in shaft 100；

Example IV

The axis body of shaft, the shaft is structure as a whole, and the shaft is horizontally disposed or vertically arranged；

Motor, compressor, turbine, thrust bearing and two transverse bearings being set in the shaft, described two diameters It is non-contact type bearing to bearing；

And first casing and the second casing, first casing connect with second casing；

Wherein, the motor, the thrust bearing and described two transverse bearings are all set in first casing, institute It states compressor and the turbine is all set in second casing；The impeller of the impeller of the compressor and the turbine is in institute It states in the second casing mutually by setting.

With the raising of rotor speed, contact bearing has been unable to satisfy high turn since there are biggish mechanical wears The needs of fast rotor.Therefore, in the utility model embodiment, in order to adapt to the growth requirement of rotor high-speed rotation, transverse bearing Non-contact type bearing can be used.

In the utility model embodiment, the first casing and the second casing can be positioned and be connected by seam allowance (not shown) It connecing, wherein thrust bearing and all transverse bearings can be provided entirely in the first casing (can be understood as motor casing), And no setting is required bearing in the second casing (can be understood as gas turbine casing).In this way, need to only guarantee to be used in the first casing The machining accuracy at the position of bearing stator is set, is passed through in the first casing for connecting the position of bearing stator in assembly The processing that is once loaded can be completed, it is seen then that and the utility model reduces the machining accuracy and assembly precision of gas turbine motor group, It reduces costs, is suitble to engineering batch production.

In the utility model embodiment, shaft can be horizontally disposed with, can also be vertically arranged, accordingly, it is to be understood that ground, this The rotor-support-foundation system of utility model embodiment is not only suitable for needing the horizontal unit using rotor-support-foundation system, is also applied for needing to use turning The vertical unit of subsystem, such as Horizontal gas expander motor group or Verticle gas expander motor group.

In the utility model embodiment, since the axis body of shaft is structure as a whole, so that middle use be different from the prior art Gas turbine rotor and rotor are attached by shaft coupling.Compared with prior art, since the axis body of shaft is integrated knot Structure, the intensity of axis body is with uniformity everywhere in shaft, this makes setting position of the thrust bearing in shaft unrestricted.

In the utility model embodiment, by by the impeller of the impeller of compressor and turbine mutually by setting so that the first machine Axial length in casket shortens, so as to further increase the stability of entire rotor-support-foundation system.

Further, to reduce influence of the heat to compressor efficiency that turbine generates, can on the turbine of turbine and/ Or thermal insulation layer (not shown) is set, wherein the material of thermal insulation layer can be aeroge or heat-proof quality on the compressor Good other materials；The turbine of turbine can also be using the lower material manufacture of thermal coefficient, for example, being manufactured with ceramic material The turbine of turbine.

As shown in figure 15, the utility model embodiment provides a kind of rotor-support-foundation system, including shaft 100 and thrust bearing 500, The axis body of shaft 100 is structure as a whole, and shaft 100 is horizontally disposed；

Motor 200, compressor 300, turbine 400, thrust bearing 500, the first transverse bearing being set in shaft 100 600 and second transverse bearing 700, the first transverse bearing 600 and the second transverse bearing 700 are non-contact type bearing, wherein One transverse bearing 600 and thrust bearing 500 are integrated, form integrated form bearing 10000；

And first casing 800 and the second casing 900, the first casing 800 connect with the second casing 900, wherein motor 200, thrust bearing 500, the first transverse bearing 600 and the second transverse bearing 700 are all set in the first casing 800, compressor 300 and turbine 400 be all set in the second casing 900.

First transverse bearing 600 is set to the side far from the second casing 900 of motor 200, and the second transverse bearing 700 is set It is placed in the side close to the second casing 900 of motor 200；Thrust bearing 500 is set to the first transverse bearing 600 and motor 200 Between.

Accordingly, it is considered to the high-revolving growth requirement of gas turbine motor group be arrived, in order to improve thrust bearing and transverse bearing Working performance, in the utility model embodiment, the first transverse bearing 600 can be dynamic using gas magnetic hybrid radial bearing or gas Static pressure hybrid radial bearing；Second transverse bearing 700 can be radial using gas magnetic hybrid radial bearing or gas hybrid Bearing.

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

In the utility model embodiment, in general, the weight of motor 200 and thrust bearing 500 is larger, entire rotor The center of gravity of system can be partial to 600 side of the first transverse bearing.In consideration of it, the bearing capacity for improving the second transverse bearing 700 helps In the stability for improving entire rotor-support-foundation system.

In the utility model embodiment, compressor 300 can be centrifugal compressor 300, the turbine of turbine 400 can for from Core type turbine；Motor 200 is Hydrodynamic bearing electric machine, and the position of the bearing of the correspondence motor 200 of shaft 100 can be set first Dynamic pressure generation trough 201.

Further, motor 200 can also be starting-generating integrated motor.

In this way, motor 200 can be opened with start-up mode, in rotor-support-foundation system initial start time so that rotor-support-foundation system Rotation, after the revolving speed of rotor-support-foundation system is promoted to preset rotation speed, can be switched to power generation mode for the operating mode of motor 200.

As shown in figure 16, the utility model embodiment provides another rotor-support-foundation system, including shaft 100 and thrust bearing 500, the axis body of shaft 100 is structure as a whole, and shaft 100 is vertically arranged；

Remaining can refer to the related description in Figure 11, and can reach identical technical effect, and to avoid repeating, this is practical New embodiment does not repeat this.

Embodiment five

When the rotor-support-foundation system of the application is in mobile device, such as stroke-increasing electric automobile, in rotor-support-foundation system not work In the case where work, shaft is directly contacted with bearing.Automobile in the process of moving, due to jolt or vibrate cause shaft relative to The movement of bearing radially or axially so that generating abrasion between shaft and bearing, and then influences precision and the service life of bearing.

Therefore, to solve the above-mentioned problems, on the basis of the utility model other embodiments, the utility model embodiment Rotor-support-foundation system be arranged locking device, the locking device be used for when rotor-support-foundation system does not work, lock shaft.

In the utility model embodiment, the structure type and set-up mode of locking device is not unique, for ease of understanding, under Face combines Fig. 9 that two kinds of embodiments for being provided with locking device in rotor-support-foundation system are specifically described.

Under a kind of embodiment, as shown in figure 17, locking device 110 includes flexible holding out against unit 111,112 and of connecting rod Fixation member 113, one end of connecting rod 112 are connected and fixed component 113, and other end connection is flexible to hold out against unit 111, flexible to hold out against The end face of one end of the separate turbine 400 of 111 face shaft 100 of unit, the other end of fixation member 113 are fixedly attached to installation The shell of the rotor-support-foundation system of the application.

When rotor-support-foundation system is shut down, the flexible of locking device 110 holds out against the movement of unit 111, and pushes away along the axial direction of shaft 100 Turn axis 100, so that the stator of thrust bearing 500 is contacted with thrust disc, thus by 100 axial restraint of shaft, while utilizing and pushing away Frictional force between the stator and thrust disc of power bearing 500 is radially fixed by shaft 100.

Further, it stretches and holds out against unit 111 and be provided with top tip part (not shown), the separate turbine 400 of shaft 100 The end face of one end be provided with center hole (not shown).In the locked condition, top tip part heads into the center hole of shaft 100, So as to preferably fix shaft 100, prevent from causing the abrasion to shaft 100 and bearing in the driving process of vehicle And damage.

Under another embodiment, as shown in Figure 18 to Figure 19, locking device 120 may be set to be the lock of ferrule structure Tight device.Specifically, locking device 120 includes telescopic unit 121 and cutting ferrule 122, cutting ferrule 122 is connected to telescopic unit 122 Telescopic end.Cutting ferrule 122 can be semicircle cutting ferrule, radius be equal to or less times greater than shaft 100 radius, the axis of cutting ferrule 122 Line and the axis of shaft 100 are arranged in parallel, and telescopic unit 121 is installed to the substantially axial middle position of shaft 100, and fixed company It is connected to the shell of the rotor-support-foundation system of installation the application.

When rotor-support-foundation system is shut down, telescopic unit 121 stretches out, and so that cutting ferrule 122 is blocked shaft 100, and shaft 100 is pushed It is contacted to transverse bearing, thus shaft 100 is radially fixed, while will be turned using the frictional force of transverse bearing and shaft 100 100 axial restraint of axis.

Further, telescopic unit 121 can choose the portion of the achievable extension and contraction control such as piston type cylinder or hydraulic cylinder Part.

In this embodiment, setting position of the locking device 120 in shaft 100 can be not construed as limiting, it is preferable that lock Tight device 120 is set between two farthest transverse bearings in rotor-support-foundation system.

It should be noted that the locking device in Figure 17 and Figure 18 is based on the setting of the rotor-support-foundation system shown in Figure 13, for Locking device is set in the rotor-support-foundation system of the utility model other embodiments, is not described one by one herein.

In the utility model embodiment, by the way that locking device is arranged, when rotor-support-foundation system does not work, locking device can be locked Tight shaft.In such manner, it is possible to prevent the movement of shaft radially or axially relative to bearing, so as to improve bearing precision and Service life.

Embodiment six

Therefore, to solve the above-mentioned problems, on the basis of the utility model other embodiments, the utility model embodiment Rotor-support-foundation system, be coated with anti-abrasive coatings 101 at the position of the installation bearing of shaft 100, as shown in figure 19.

Anti-abrasive coatings 101 are coated at the position of the installation bearing of shaft 100, shaft 100 and bearing can be effectively prevented Abrasion.The anti-abrasive coatings 101 preferentially select chemical stability, corrosion resistance, high lubrication and non-stickiness and good anti-aging endurance Material, such as polytetrafluoroethylene (PTFE) etc..

It should be noted that the anti-abrasive coatings 101 in Figure 19 are arranged based on the rotor-support-foundation system shown in Figure 13, in this reality Locking device is set in the rotor-support-foundation system with novel other embodiments, is not described one by one herein.

Embodiment seven

With the bearing of the utility model embodiment, (wherein, the first magnetic part in the first magnetic bearing is the first electricity below Magnet, the second magnetic part in the second magnetic bearing are the second electromagnet) control method in rotor-support-foundation system carries out in detail Explanation.

As shown in figure 21, the utility model embodiment provides a kind of control method of bearing, including：

S1011, the first magnetic bearing and the second magnetic bearing are opened.

S1012, control shaft moving in the radial direction in shaft under the magneticaction of multiple first magnetic parts, with Shaft is set to be moved to preset radial position；And control thrust disc is between multiple second magnetic parts and third magnetic part Magneticaction under moved on the axial direction of shaft so that between the second magnetic bearing in thrust disc and the first stator The difference in the second gap between the second magnetic bearing in two gaps and thrust disc and the second stator is less than or equal to predetermined value.

S1013, shaft revolving speed accelerate to after working speed, close the first magnetic bearing and the second magnetic bearing.

When S1014, rotor-support-foundation system are shut down, the first magnetic bearing and the second magnetic bearing are opened.

S1015, shaft revolving speed be decelerated to after zero, close the first magnetic bearing and the second magnetic bearing.

In above process, after the first magnetic bearing and the second magnetic bearing are opened, work of the shaft in multiple first magnetic parts With lower picking-up and reach preset radial position (radial position of shaft can be detected by displacement sensor), and, Thrust disc reaches the first stator and the second stator under the magneticaction between multiple second magnetic parts and third magnetic part Between predetermined position.With the rotation of shaft, shaft starts turning in the case that air-flow lubricates in by the first gap, to prevent Only wear；Opposite first stator and the second stator start turning thrust disc in the case where air-flow lubrication in by the second gap, with It prevents from wearing.

Wherein, the first magnetic bearing and the detailed process of the second magnetic bearing unlatching are：It is inputted to first coil and the second coil The current signal of predetermined value.

As the revolving speed of shaft is increasing, when the revolving speed of shaft reaches working speed, radial sub- bearing and thrust (gas dynamic pressure that the first gap forms radial sub- bearing is arranged in the aero dynamic bearing of bearing between the first magnetic bearing and shaft The aero dynamic bearing that the second gap forms the sub- bearing of thrust is arranged in bearing between thrust disc and stator) generate air film pressure Power can stablize shaft and thrust disc, can close the first magnetic bearing and the second magnetic bearing at that time.

When rotor-support-foundation system is shut down, shaft is slowed down, in order to make shaft keep stablizing in entire rotor-support-foundation system stopping process, The first magnetic bearing and the second magnetic bearing are opened when rotor-support-foundation system is shut down, and the first magnetic can be closed after shaft is stopped completely Bearing and the second magnetic bearing.

As shown in figure 22, the utility model embodiment also provides the control method of another bearing, including：

S1021, the first magnetic bearing and the second magnetic bearing are opened.

S1022, control shaft moving in the radial direction in shaft under the magneticaction of multiple first magnetic parts, with Shaft is set to be moved to preset radial position；And control thrust disc is between multiple second magnetic parts and third magnetic part Magneticaction under moved on the axial direction of shaft so that between the second magnetic bearing in thrust disc and the first stator The difference in the second gap between the second magnetic bearing in two gaps and thrust disc and the second stator is less than or equal to predetermined value.

S1023, shaft revolving speed accelerate to after the first preset value, close the first magnetic bearing and the second magnetic bearing.

When S1024, rotor-support-foundation system accelerate to single order critical speed or second order critical speed, the first magnetic bearing and second is opened Magnetic bearing.

Specifically, when the gas flow rate of the first gap location between shaft and the first magnetic bearing reach single order critical speed or When second order critical speed, the first magnetic bearing and the second magnetic bearing are opened, until shaft is restored to equilbrium position.

Optionally, when rotor-support-foundation system accelerates to single order critical speed or second order critical speed, the first magnetic bearing and the are opened Two magnetic bearings, including：

When rotor-support-foundation system accelerates to single order critical speed or second order critical speed, the first magnetic bearing and the second magnetic bearing are controlled It is opened with maximum power；Alternatively,

When rotor-support-foundation system accelerates to single order critical speed or second order critical speed, the first magnetic bearing and the second magnetic bearing are controlled It is opened in a manner of stroboscopic according to predeterminated frequency.

S1025, rotor-support-foundation system are steadily spent after single order critical speed or second order critical speed, close the first magnetic bearing and Second magnetic bearing.

In S1026, rotor-support-foundation system stopping process, when rotor-support-foundation system is decelerated to single order critical speed or second order critical speed When, open the first magnetic bearing and the second magnetic bearing.

Specifically, when the gas flow rate of the first gap location between shaft and the first magnetic bearing is decelerated to single order critical speed Or when second order critical speed, the first magnetic bearing and the second magnetic bearing are opened, until shaft is restored to equilbrium position.

Optionally, when rotor-support-foundation system is decelerated to single order critical speed or second order critical speed, the first magnetic bearing and the are opened Two magnetic bearings, including：

When rotor-support-foundation system is decelerated to single order critical speed or second order critical speed, the first magnetic bearing and the second magnetic bearing are controlled It is opened with maximum power；Alternatively,

When rotor-support-foundation system is decelerated to single order critical speed or second order critical speed, the first magnetic bearing and the second magnetic bearing are controlled It is opened in a manner of stroboscopic according to predeterminated frequency.

S1027, rotor-support-foundation system are steadily spent after single order critical speed or second order critical speed, close the first magnetic bearing and Second magnetic bearing.

Revolving speed when being decelerated to the second preset value of S1028, shaft, open the first magnetic bearing and the second magnetic bearing.

S1029, shaft revolving speed be decelerated to after zero, close the first magnetic bearing and the second magnetic bearing.

As the revolving speed of shaft is increasing, when shaft revolving speed reach the first preset value, such as rated speed 5% to When 30%, (the first gap is arranged in the aero dynamic bearing of radial sub- bearing and the sub- bearing of thrust between the first magnetic bearing and shaft The aero dynamic bearing for forming radial sub- bearing, is arranged the second gap and forms the sub- bearing of thrust between thrust disc and stator Aero dynamic bearing) gas film pressure that generates can stablize shaft and thrust disc, the first magnetic bearing and the can be closed at that time Two magnetic bearings.

In rotor-support-foundation system stopping process, the revolving speed of shaft is smaller and smaller, when the revolving speed of shaft is lower than the second preset value, example As rated speed 5% to 30% when, at this point, the air film pressure that the aero dynamic bearing of radial sub- bearing and the sub- bearing of thrust generates Power is also slowed down with shaft or thrust disc and is reduced, therefore, it is necessary to open the first magnetic bearing and the second magnetic bearing, so as to shaft and push away Power disk keeps stablizing, and can close the first magnetic bearing and the second magnetic bearing after being zero until the speed of shaft.

Optionally, the above method further includes：

When the first gap between shaft and the first magnetic bearing changes, the first magnetic bearing is opened, makes shaft more Under the magneticaction of a first magnetic part to far from gap become smaller side direction it is mobile；

Shaft is in after balance radial position, closes the first magnetic bearing.

When load is supported in shaft, it is gradually reduced shaft and when close to the first magnetic bearing of lower section, first sensor (the preferred pressure sensor of first sensor here) obtains the signal that air pressure increases, and the first magnetic bearing needs to intervene work at this time Make.First magnetic bearing by magneticaction in making it suspend in shaft upwards, when shaft reaches new balance radial position, first Magnetic bearing stops working.

When there is external impact disturbance to occur, shaft may be rapidly close to the first magnetic bearing, it is likely that leads to shaft The first gap moment between the first magnetic bearing is too small, makes the local gas flow velocity at the first gap reduction close to even up to Velocity of sound, so that causing shock wave generates Pneumatic hammer phenomenon.The generation of shock wave will lead to local gas flow and disturbance and confusion occur, When fluid velocity is remarkably decreased in velocity of sound to its pressure when changing between subsonic speed in staged.In this case, it needs to control First magnetic part of the first magnetic bearing is opened in turn with predeterminated frequency, to provide the damping action to disturbance, to effectively press down External disturbance processed.When shaft is restored to after new balance radial position, the first magnetic bearing stops working.

In above process, the advantages of facilitating real-time control using the first magnetic bearing, the uneven matter of active balancing shaft Amount or shaft whirling motion etc. lead to the factor of shaft over-deflection, are fixed on shaft in radial directions in a certain very low range. In addition, the position (i.e. linear velocity supersonic speed position) for generating shock wave can be accurately positioned, and pass through in the accelerator of shaft Size of current and the direction etc. for controlling the first magnetic bearing, make the first magnetic bearing generate opposite power to balance Shock Wave.Wait swash After popin is steady, the control strategy of the first magnetic bearing is adjusted again, and shaft is fixed on a certain very low range in a manner of most energy-efficient It is interior.

Optionally, the above method further includes：

When load is supported on thrust disc, thrust disc is moved on the axial direction of shaft under the action of load loads, is pushed away The second magnetic bearing in the second gap between the second magnetic bearing and thrust disc and the second stator in power disk and the first stator it Between the second gap difference be greater than predetermined value when, open the second magnetic bearing；

When in the second gap and thrust disc and the second stator between the second magnetic bearing in thrust disc and the first stator The difference in the second gap between the second magnetic bearing is less than or equal to predetermined value, closes the second magnetic bearing.

When load is supported on thrust disc, make between thrust disc and the first stator or the second magnetic bearing of the second stator Two gaps become smaller and when close to the second magnetic bearings of the side, second sensor (the preferred pressure sensor of second sensor here) The signal that air pressure increases is obtained, the second magnetic bearing needs to intervene work at this time.Second magnetic bearing by magneticaction on thrust disc, Keep it mobile to the second magnetic bearing of the other side, when thrust disc reaches new equilbrium position, the second magnetic bearing can stop work Make.

Specifically, if the second gap between the second magnetic bearing in thrust disc and the first stator is less than thrust disc and second The second gap between the second magnetic bearing in stator, and between second between the second magnetic bearing in thrust disc and the first stator The difference in the second gap between the second magnetic bearing in gap and thrust disc and the second stator is greater than predetermined value, then it is fixed to control second The second magnetic bearing in son makes under magneticaction of the thrust disc between the first magnetic part and multiple second magnetic parts, court It is moved on the axial direction of shaft in direction far from the second stator.

If the second gap between the second magnetic bearing in thrust disc and the second stator is less than in thrust disc and the first stator The second magnetic bearing between the second gap, and the second gap between the second magnetic bearing in thrust disc and the first stator with push away The difference in the second gap between the second magnetic bearing in power disk and the second stator is greater than predetermined value, then controls in the first stator Second magnetic bearing makes under magneticaction of the thrust disc between the first magnetic part and multiple second magnetic parts, towards far from the It is moved on the axial direction of shaft in the direction of one stator.

Optionally, when load is supported on thrust disc, thrust disc is under the action of load loads on the axial direction of shaft It is mobile, the second gap between the second magnetic bearing in thrust disc and the first stator and the second magnetic in thrust disc and the second stator When the difference in the second gap between bearing is greater than predetermined value, the second magnetic bearing in the first stator or the second stator, packet are opened It includes：

When load is supported on thrust disc, thrust disc is moved on the axial direction of shaft under the action of load loads, is pushed away The second magnetic bearing in the second gap between the second magnetic bearing and thrust disc and the second stator in power disk and the first stator it Between the difference in the second gap when being greater than predetermined value, control the second magnetic bearing in the first stator or the second stator with maximum power It opens；Alternatively,

When load is supported on thrust disc, thrust disc is moved on the axial direction of shaft under the action of load loads, is pushed away The second magnetic bearing in the second gap between the second magnetic bearing and thrust disc and the second stator in power disk and the first stator it Between the difference in the second gap when being greater than predetermined value, control the second magnetic bearing in the first stator or the second stator according to default frequency Rate is opened in a manner of stroboscopic.

When there is external impact disturbance to occur, thrust disc may be rapidly close to certain the second magnetic bearing of side, it is likely that leads It causes the second gap moment of the side too small, makes the local gas flow velocity of second gap location of side close to even up to velocity of sound, thus Cause shock wave and generates Pneumatic hammer phenomenon.The generation of shock wave will lead to local gas flow and disturbance and confusion occur, when fluid speed Degree is remarkably decreased in velocity of sound to its pressure when changing between subsonic speed in staged.In this case, it needs to control the first stator It is opened in turn with the second magnetic bearing in the second stator with predeterminated frequency, to provide the damping action to disturbance, to effectively press down External disturbance processed.After thrust disc comes back to equilibrium state, the second magnetic bearing stops working.

In above process, the advantages of facilitating real-time control using the second magnetic bearing, the imbalance of active balancing thrust disc Quality or thrust disc whirling motion etc. lead to the factor of thrust disc over-deflection, and thrust disc is made to be fixed on certain on the axial direction of shaft In one very low range.In addition, in the accelerator of thrust disc, it can be accurately positioned and generate the position of shock wave (i.e. linear velocity is super Velocity of sound position), and by the size of current of the second magnetic bearing of control and direction etc., so that the second magnetic bearing is generated opposite Li Laiping Weigh Shock Wave.After shock wave is steady, the control strategy of the second magnetic bearing is adjusted again, is consolidated thrust disc in a manner of most energy-efficient It is scheduled in a certain very low range.

In the utility model embodiment, magnetic bearing (wherein, the first magnetic in the first magnetic bearing is provided with simultaneously for bearing Property component be the first electromagnet, the second magnetic part in the second magnetic bearing is the second electromagnet) and aerostatic bearing (bearing Static pressure air inlet restriction hole is provided on shell) in the case where, magnetic bearing and aerostatic bearing can be mutually spare, wherein a side Failure, in the case where failing or being unable to satisfy unlocking condition, another party can be used as replacement bearing and serve the same role.Example Such as, in the case where detecting magnetic bearing failure, control external air source is opened to substitute magnetic bearing and execute corresponding movement, thus Improve the safety and reliability of bearing.

Specifically, may include that mode is implemented as follows：

When first magnetic bearing and second magnetic bearing are in malfunction, external air source is opened, by described Static pressure air inlet restriction hole conveys gas to first gap and second gap location；

The shaft moving radially along the shaft under the action of gas is controlled, so that the shaft is moved to Preset radial position；And control the thrust disc and moved on the axial direction of the shaft under the action of gas, So that second gap between the second magnetic bearing in the thrust disc and first stator be equal to the thrust disc with Second gap between the second magnetic bearing in second stator.

When above embodiment respective rotor system open stage, when the first magnetic bearing and the second magnetic bearing are in failure shape When state, the control method of bearing.The control method in stages other for rotor-support-foundation system, can be by opening or closing external air source Realize that the control to bearing is not specifically described due to being readily appreciated that.

Optionally, described when first magnetic bearing and second magnetic bearing are in normal condition, open described the The step of one magnetic bearing and second magnetic bearing, including：

When first magnetic bearing and second magnetic bearing are in normal condition, first magnetic bearing and institute are opened The second magnetic bearing is stated, and opens external air source, by static pressure air inlet restriction hole between first gap and described second Gas is conveyed at gap；

The control shaft is under the magneticaction of the multiple first magnetic part in the radial direction side of the shaft It moves up, so that the shaft is moved to preset radial position；And the thrust disc is controlled in the multiple second magnetism It is moved on the axial direction of the shaft under magneticaction between component and the third magnetic part, so that the thrust Second gap between the second magnetic bearing in disk and first stator is equal to the thrust disc and second stator In the second magnetic bearing between second gap the step of, including：

The shaft is controlled in the magneticaction of the multiple first magnetic part and under the influence of gas described Shaft moves in the radial direction, so that the shaft is moved to preset radial position；And the thrust disc is controlled described Magneticaction between multiple second magnetic parts and the third magnetic part and under the influence of gas in the shaft Axial direction on move so that second gap between the second magnetic bearing in the thrust disc and first stator Equal to second gap between the second magnetic bearing in the thrust disc and second stator.

In this way, this can be further increased by using the embodiment for opening magnetic bearing and aerostatic bearing simultaneously The bearing capacity of the bearing of utility model embodiment.

In addition, when magnetic bearing is in normal condition, can also unlatching aerostatic bearing, it is right due to being readily appreciated that This is not repeated.

In summary, the preferred embodiment in the utility model has the advantages that：

First, magnetic bearing and gas bearing cooperate, improve dynamic property of the bearing under the state of running at high speed and Stability resists disturbed kinetic force strong, and then improves the bearing capacity of bearing.Meanwhile magnetic bearing is nested with gas bearing use Structure simplifies structure, and integrated level is high, and easy processing, manufacture and operation improve the comprehensive performance of bearing.It is opened in rotor-support-foundation system When opening or shutting down, shaft can be made to rotate with magnetic bearing, improve the low-speed performance of bearing, extend the service life of bearing, It can be improved the safety and reliability of bearing and whole system.

Second, relative to traditional gas hybrid diameter combined using aerostatic bearing and aero dynamic bearing To sub- bearing, the sub- bearing of the radial direction of the utility model embodiment has the advantages that fast response time.

Third, increasing aerostatic bearing, dynamic and static pressure-sub- bearing of magnetic hybrid radial is formed, is provided with magnetic axis at the same time In the case where holding with aerostatic bearing, the bearing capacity of bearing is further increased, and magnetic bearing and aerostatic bearing can be mutual Spare, in the case where wherein side's failure, failing or being unable to satisfy unlocking condition, another party can be used as replacement bearing and play Identical effect.For example, control system controls aerostatic bearing and opens to substitute magnetic the case where detecting magnetic bearing failure Bearing executes corresponding movement, to improve the safety and reliability of bearing.

In the application, the transverse bearing (the second transverse bearing 700 as shown in Figure 13) that is separately provided in rotor-support-foundation system Multiple structural forms can be used, if transverse bearing uses gas magnetic hybrid radial bearing, can be paillon formula gas magnetic mixing diameter To bearing, it is also possible to slot type gas magnetic hybrid radial bearing.

With reference to the accompanying drawing respectively to the specific constructive form of above two transverse bearing, and in entire rotor-support-foundation system control Specific control process in system is described in detail.

Embodiment eight

Figure 23 to Figure 30 is the structural schematic diagram of paillon formula gas magnetic hybrid radial bearing provided by the embodiment of the utility model.

As shown in Figure 23 to Figure 30, paillon formula gas magnetic hybrid radial bearing 6100 includes：

The third magnetic bearing 6101 being sheathed in shaft 100, it is circumferentially arranged on third magnetic bearing 6101 to have multiple five Magnetic part；

It is sheathed in shaft 100, and the second foil bearing 6102 between third magnetic bearing 6101 and shaft 100, Second foil bearing 6102 is equipped with the 6th magnetic part that magnetic force can be generated between multiple 5th magnetic parts；

Wherein, there is third space 6103, and the second foil bearing 6102 between the second foil bearing 6102 and shaft 100 It can be in moving in the radial direction in shaft 100 under the magneticaction of multiple 5th magnetic parts and the 6th magnetic part.

In the utility model embodiment, by the way that third space 6103 and third magnetic bearing are arranged in transverse bearing 6100 6101, so that the transverse bearing 6100 be made to form gas, magnetic hybrid radial bearing.

When work, the gas bearing in transverse bearing 6100 can cooperate with third magnetic bearing 6101, in radial axle When holding 6100 in stable working condition, realizes and support by gas bearing；And it is in non-stable in transverse bearing 6100 When working condition, transverse bearing 6100 is controlled and responded in time by third magnetic bearing 6101.

As it can be seen that the utility model embodiment can improve transverse bearing, the especially dynamic property under the state of running at high speed And stability, resist disturbed kinetic force strong, and then improve the bearing capacity of transverse bearing.The radial axle of the utility model embodiment It holds and can satisfy high-revolving rotor-support-foundation system, for example, the demand of gas turbine or gas turbine power generation Unit erriger etc..

In the utility model embodiment, since silicon steel sheet or silicon steel sheet have the physics such as magnetic conductivity is high, eddy-current loss is low special Property, shaft 100 can be overrided to form by several silicon steel sheets or silicon steel sheet.

Optionally, multiple 5th magnetic parts include multiple third permanent magnets, and multiple third permanent magnets are in third magnetic bearing It is circumferentially arranged on 6101；

Alternatively, multiple 5th magnetic parts include multiple third electromagnet, multiple third electromagnet are in third magnetic bearing Circumferentially arranged on 6101, each third electromagnet in multiple third electromagnet includes being set on third magnetic bearing 6101 Third magnetic core 61011 and the tertiary coil 61012 being wound on third magnetic core 61011.

In the utility model embodiment, when paillon formula gas magnetic hybrid radial bearing 6100 only needs magnetic part to provide magnetic force When without magnetic control, the preferred third permanent magnet of the 5th magnetic part；When paillon formula gas magnetic mixing thrust bearing needs magnetic force simultaneously When with magnetic control, the preferred third electromagnet of the 5th magnetic part.

When the 5th magnetic part is third electromagnet, electric current is passed through toward tertiary coil 61012, it can make third magnetic core 61011 generate magnetic force.The of different sizes of electric current, the magnetic force size that third magnetic core 61011 generates are passed through toward tertiary coil 61012 It is different；It is passed through sense of current difference toward tertiary coil 61012, the magnetic pole of third magnetic core 61011 is also different.

Wherein, since silicon steel sheet or silicon steel sheet have the physical characteristics such as magnetic conductivity is high, eddy-current loss is low, the utility model In preferred embodiment, third magnetic core 61011 can be overrided to form by several silicon steel sheets or silicon steel sheet.

Optionally, third magnetic bearing 6101 includes：

Third magnetic bearing seat 61013, third magnetic bearing seat 61013 are sheathed in shaft 100, third magnetic bearing seat 61013 Above circumferentially arranged to have multiple third holding tanks 61014, multiple 5th magnetic parts are set to multiple third holding tanks 61014 It is interior, and the side where the magnetic pole of multiple 5th magnetic parts towards the second foil bearing 6102；

The first bearing shell 61015 being sheathed on outside third magnetic bearing seat 61013；

The first axle bearing sleeve 61016 being sheathed between third magnetic bearing seat 61013 and the second foil bearing 6102；

And it is respectively arranged at the third end cap 61017 and the 4th end cap 61018 at 61015 both ends of first bearing shell；

Wherein, first axle bearing sleeve 61016, third end cap 61017 and the cooperation of the 4th end cap 61018, it is magnetic by multiple five Component is fixed on third magnetic bearing seat 61013.

Wherein, since silicon steel sheet or silicon steel sheet have the physical characteristics such as magnetic conductivity is high, eddy-current loss is low, the utility model In preferred embodiment, third magnetic bearing seat 61013 can be overrided to form by several silicon steel sheets or silicon steel sheet.Third holding tank 61014 quantity can be but be not limited to six or eight, and the circumferential direction along third magnetic bearing seat 61013 is uniformly arranged.In this way, The magnetic force between third magnetic bearing 6101 and the second foil bearing 6102 can be made more uniform, stable.It should be noted that more A 5th magnetic part can also be set on third magnetic bearing seat 61013 using other modes, to this without limiting.Third The material of end cap 61017 and the 4th end cap 61018 may each be non-magnetic material, preferably duralumin material.First axle bearing sleeve 61016 Material can be non-magnetic material, preferably duralumin material.The material of first bearing shell 61015 can be non-magnetic material, excellent Select duralumin material.

Optionally, the second foil bearing 6102 includes third paillon 61021 and the 4th paillon 61022, third paillon 61021 It is installed on first axle bearing sleeve 61016, the 4th paillon 61022 is stacked at the side of the close shaft 100 of third paillon 61021；

Wherein, the 4th paillon 61022 is flat paillon, and the 6th magnetic part is set on the 4th paillon 61022, so that the 4th Paillon 61022 can be under the magneticaction of multiple 5th magnetic parts and the 6th magnetic part in the radial direction of shaft 100 Upper movement；Third paillon 61021 is the flexible deformation paillon that flexible deformation can occur when the 4th paillon 61022 is mobile.

Wherein, third paillon 61021 is flexible deformation paillon, it is contemplated that the material of permeability magnetic material is harder and crisp, should not make For flexible deformation paillon, therefore, the preferably non-magnetic stainless steel band of third paillon 61021.

In the utility model embodiment, by setting flat paillon for the 4th paillon 61022, convenient for the 4th paillon of control The distance between 61022 and shaft 100, in other words, convenient for controlling the size of third space 6103.

Optionally, third paillon 61021 is flexible deformation paillon wave-shaped, and third paillon 61021 is not close Annular, which is provided with an opening, one end of opening is fixing end, and fixing end is fixed on first axle bearing sleeve 61016, opening The other end is movable end；

Wherein, ripple glaze of the 4th paillon 61022 in shaft 100 when moving in the radial direction, on third paillon 61021 Stretching, extension is shunk, and movable end is moved along the circumferential direction of annular.

In the utility model embodiment, by setting flexible deformation paillon wave-shaped for third paillon 61021, just In stretching, extension or shrinkage character using ripple glaze, the 4th paillon 61022 moving in the radial direction in shaft 100 is pushed.

It should be noted that the shape of the third paillon 61021 in the utility model embodiment be not limited to it is wavy, Other shapes that can generate flexible deformation can be adapted for the third paillon 61021 of the utility model embodiment.

Optionally, the 6th magnetic part includes the side for being set to the close first axle bearing sleeve 61016 of the 4th paillon 61022 Third magnetic material 61023 on surface；

Wherein, the distribution in a strip shape on the 4th paillon 61022 of third magnetic material 61023, and it is magnetic to form multiple strips The length direction in portion, multiple strip magnetic portions is parallel with the axis direction of shaft 100；

Alternatively, third magnetic part is in spot distribution on the 4th paillon 61022.

Wherein, the preferred non-magnet material of material of the 4th paillon 61022 hides spray third on the surface of the 4th paillon 61022 After magnetic material 61023, third magnetic material 61023 can be covered with ceramic coating.4th paillon 61022 can be by using 40% zirconium oxide, 30% alpha-aluminium oxide and 30% magnesium aluminate spinels ceramic nano micro mist sintering be made.

If third magnetic material 61023 is completely covered in the surface of the 4th paillon 61022, third magnetism material will increase dramatically The magnetic force generated between material 61023 and the first magnetic part, is easy to cause the 4th paillon 61022 to deform in this way.In view of This, in the utility model embodiment, by hiding spray third magnetic material 61023 on the surface of the 4th paillon 61022, makes third magnetic Property material 61023 distribution in a strip shape or spot distribution on the 4th paillon 61022, can be by third magnetic material 61023 and The magnetic force generated between one magnetic part is controlled in reasonable range, to avoid the 4th paillon 61022 due to excessive magnetic force It deforms.

Optionally, paillon formula gas magnetic hybrid radial bearing 6100 further includes being provided at circumferentially spaced along third magnetic bearing 6101 Multiple 3rd sensors 6104, wherein each 3rd sensor 6104 include 3rd sensor lid 61041 and 3rd sensor The first end of probe 61042,3rd sensor probe 61042 connects 3rd sensor lid 61041,3rd sensor lid 61041 It is fixed on third magnetic bearing 6101, on first bearing shell 61015, third magnetic bearing seat 61013 and first axle bearing sleeve 61016 Equipped with the through-hole for being passed through for 3rd sensor probe 61042；The second end of 3rd sensor probe 61042 passes through first axle Hold the through-hole on shell 61015, third magnetic bearing seat 61013 and first axle bearing sleeve 61016, and extend to first axle bearing sleeve 61016 with In gap between third paillon 61021, and the second end end of 3rd sensor probe 61042 and first axle bearing sleeve 61016 Close third paillon 61021 side it is concordant.

It, can be at real-time detection third paillon 61021 by the way that 3rd sensor 6104 is arranged in the utility model embodiment Gas pressure parameter.In this way, third magnetic bearing 6101 can be according to the testing result of 3rd sensor 6104 to transverse bearing 6100 carry out active control, and control can be made to reach higher precision.

In the utility model embodiment, by the structure type and mounting means of above-mentioned 3rd sensor 6104, it can make 3rd sensor 6104 is more stably set on third magnetic bearing 6101.In addition, by the second of 3rd sensor probe 61042 Hold end concordant with the side of close third paillon 61021 of first axle bearing sleeve 61016, on the one hand, to can be avoided third sensing Device probe 61042 is touched by third paillon 61021, to be conducive to protect 3rd sensor probe 61042；Another party Face will not have an impact the air film in third space 6103, the air film in third space 6103 is avoided to disturb.

Optionally, in multiple 3rd sensors 6104, each 3rd sensor 6104 is respectively arranged at adjacent two Between five magnetic parts.

In the utility model embodiment, the quantity of 3rd sensor 6104 can be identical as the quantity of the 5th magnetic part, Each 3rd sensor 6104 is respectively arranged between two adjacent the 5th magnetic parts, and each 3rd sensor 6104 is preferably It is set to the middle part of third magnetic bearing 6101.In addition, in the utility model embodiment, in addition to being arranged for detecting third paillon Except the 3rd sensor 6104 of gas pressure parameter at 61021, the displacement that may be provided for detection rotating shaft position is passed Sensor, the perhaps acceleration sensing for detecting the velocity sensor of shaft revolving speed or for detecting shaft rotary acceleration Device, etc..

Below with the paillon formula gas magnetic hybrid radial bearing of the utility model embodiment (wherein, in third magnetic bearing Five magnetic parts be electromagnet) participate in rotor-support-foundation system control process when specific control method be described in detail.

The utility model embodiment provides a kind of control method of paillon formula gas magnetic hybrid radial bearing, including：

S611, third magnetic bearing is opened, controls shaft under the magneticaction of multiple 5th magnetic parts in the diameter of shaft It is moved on direction, so that shaft is moved to preset radial position.

S612, shaft revolving speed accelerate to after working speed, close third magnetic bearing.

When S613, rotor-support-foundation system are shut down, third magnetic bearing is opened.

S614, shaft revolving speed be decelerated to after zero, close third magnetic bearing.

In above process, after third magnetic bearing is opened, shaft holds up and reaches predetermined under the action of third magnetic bearing Position has third space between the second foil bearing and shaft.

With the rotation of shaft, shaft starts turning in the case that air-flow lubricates in by third space, to prevent from wearing. Third magnetic bearing open detailed process be：To the current signal of tertiary coil input predetermined value, shaft is in third magnetic bearing It is held up under effect and reaches predetermined position.

As the revolving speed of shaft is increasing, when the revolving speed of shaft reaches working speed, the gas of the transverse bearing is dynamic Last item holds (aero dynamic bearing that the third space being arranged between the second foil bearing and shaft forms the transverse bearing) production Raw gas film pressure can stablize shaft, can close third magnetic bearing at that time.

When rotor-support-foundation system is shut down, shaft is slowed down, in order to make shaft keep stablizing in entire rotor-support-foundation system stopping process, Third magnetic bearing is opened when rotor-support-foundation system is shut down, and third magnetic bearing can be closed after shaft is stopped completely.

The utility model embodiment also provides the control method of another paillon formula gas magnetic hybrid radial bearing, including：

S621, third magnetic bearing is opened, controls shaft under the magneticaction of multiple 5th magnetic parts in the diameter of shaft It is moved on direction, so that shaft is moved to preset radial position.

S622, shaft revolving speed accelerate to after the first preset value, close third magnetic bearing.

Revolving speed when accelerating to single order critical speed or the second order critical speed of S623, shaft, open third magnetic bearing.

Specifically, the gas at the third space between shaft and the second foil bearing (further, to be the 4th paillon) When body flow velocity reaches single order critical speed or second order critical speed, third magnetic bearing is opened, until shaft restores radial to balance Position.

Optionally, when the revolving speed of shaft accelerates to single order critical speed or the second order critical speed, third magnetic axis is opened It holds, including：

When the revolving speed of shaft accelerates to single order critical speed or the second order critical speed, third magnetic bearing is controlled with maximum Power is opened；Alternatively,

When the revolving speed of shaft accelerates to single order critical speed or the second order critical speed, third magnetic bearing is controlled according to pre- If frequency is opened in a manner of stroboscopic.

S624, rotor-support-foundation system are steadily spent after single order critical speed or the second order critical speed, and third magnetic axis is closed It holds.

In S625, rotor-support-foundation system stopping process, when the rotor-support-foundation system is decelerated to the single order critical speed or described two When rank critical speed, third magnetic bearing is opened.

Specifically, the gas at the third space between shaft and the second foil bearing (further, to be the 4th paillon) When body flow velocity is decelerated to single order critical speed or second order critical speed, third magnetic bearing is opened, until shaft is restored to balance diameter To position.

Optionally, when the revolving speed of shaft is decelerated to single order critical speed or the second order critical speed, third magnetic axis is opened It holds, including：

When the revolving speed of shaft is decelerated to single order critical speed or the second order critical speed, third magnetic bearing is controlled with maximum Power is opened；Alternatively,

When the revolving speed of shaft is decelerated to single order critical speed or the second order critical speed, third magnetic bearing is controlled according to pre- If frequency is opened in a manner of stroboscopic.

S626, rotor-support-foundation system are steadily spent after the single order critical speed or the second order critical speed, and third is closed Magnetic bearing.

Revolving speed when being decelerated to the second preset value of S627, shaft, open third magnetic bearing.

S628, the shaft revolving speed be decelerated to after zero, close third magnetic bearing.

As the revolving speed of shaft is increasing, when shaft revolving speed reach the first preset value, such as rated speed 5% to When 30%, (third space being arranged between the second foil bearing and shaft forms this to the aero dynamic bearing of the transverse bearing The aero dynamic bearing of transverse bearing) generate gas film pressure can by shaft stablize, third magnetic bearing can be closed at that time.

In rotor-support-foundation system stopping process, shaft is slowed down, when the revolving speed of shaft is down to the second preset value, such as rated speed 5% to 30% when, open third magnetic bearing, third magnetic bearing can be closed after shaft is stopped completely.

Optionally, the method also includes：

When the third space between the shaft and second foil bearing (further, to be the 4th paillon) becomes When change, the third magnetic bearing is opened, gap is made to become smaller corresponding second foil bearing in side in the multiple 5th magnetic part To mobile close to the direction of the shaft under magneticaction between the 6th magnetic part；

The shaft is in after balance radial position, closes the third magnetic bearing.

When load is supported in shaft, it is gradually reduced shaft and when close to four paillon of lower section, 3rd sensor (this In the preferred pressure sensor of 3rd sensor) obtain air pressure increase signal, third magnetic bearing needs to intervene work at this time.The Three magnetic bearings use magnetic force by the 4th foil of lower section not fully directly by magneticaction in making it suspend in shaft upwards Piece pushes (i.e. to the direction close to shaft) upward, makes lower section gap reduce to improve the pressure of lower section gap location, adapts to The weight loaded in shaft redistributes the stream pressure in third space all directions automatically.When shaft reaches new balance When radial position, third magnetic bearing stops working.

When there is external impact disturbance to occur, shaft may be rapidly close to the second foil bearing, it is likely that causes to turn Gap moment between axis and the second foil bearing is too small, makes the close even up to sound of the local gas flow velocity at the reduction of gap Speed, so that causing shock wave generates Pneumatic hammer phenomenon.The generation of shock wave will lead to local gas flow and disturbance and confusion occur, when Fluid velocity is remarkably decreased in velocity of sound to its pressure when changing between subsonic speed in staged.In this case, it needs to make second Foil bearing active " evacuation " shaft, so that the gap between shaft and the second foil bearing be made to increase so that air velocity to the greatest extent may be used Between subsonic area capable of being maintained, to safeguard its normal Fluid pressure.Specifically, the two opposite sides for needing that gap is made to generate variation The 5th magnetic part magnetic pole with identical polarity excitation, i.e., the direction that gap reduces generates suction, is used for the second foil of resorption Piece bearing, the direction that gap increases generates suction, for retracting shaft.In this way, the difference using two sides magneticaction distance generates Magnetic deviation pulls shaft to restore the normal clearance between the second foil bearing, so that shaft be made to return to new balance diameter with this To position.

In above process, the advantages of facilitating real-time control using third magnetic bearing, the uneven matter of active balancing shaft Amount or shaft whirling motion etc. lead to the factor of shaft over-deflection, are fixed on shaft in radial directions in a certain very low range. In addition, the position (i.e. linear velocity supersonic speed position) for generating shock wave can be accurately positioned, and pass through in the accelerator of shaft Size of current and the direction etc. for controlling third magnetic bearing, make third magnetic bearing generate opposite power to balance Shock Wave.Wait swash After popin is steady, the control strategy of third magnetic bearing is adjusted again, and shaft is fixed on a certain very low range in a manner of most energy-efficient It is interior.

In summary, the utility model embodiment has the advantages that：

First, electromagnetic bearing and gas bearing cooperate, dynamic property of the bearing under the state of running at high speed is improved And stability, resist disturbed kinetic force strong, and then improve the bearing capacity of bearing.Meanwhile electromagnetic bearing and gas bearing use Nested structure simplifies structure, and integrated level is high, and easy processing, manufacture and operation improve the comprehensive performance of bearing.In rotor system When system starting or shutdown, the thrust disc of bearing and stator can be made to rotate in bearing clearance with electromagnetic bearing, improve bearing Low-speed performance, extend the service life of bearing, can be improved the safety and reliability of bearing and whole system.

Second, being pushed away relative to traditional gas hybrid combined using aerostatic bearing and aero dynamic bearing The paillon formula gas magnetic hybrid radial bearing of power bearing, the utility model embodiment has the advantages that fast response time.

Third, paillon can be made appropriate by the attraction of the magnetic pole of electromagnetic bearing by the way that magnetic material is arranged on paillon Deformation improves the maximum pressure for lubricating air film side in bearing and prevents lubrication flow leakage, it is anti-inclined by disturbance to improve thrust disc The heart hits the ability of wall, to also improve the bearing capacity of bearing.

Fourth, being controlled using the acquisition gas film pressure variation of lower-cost pressure sensor by simple control method The deformation of paillon, it is possible to provide damped compared with high rotor, to improve rotor stability.In addition, since control method is simple, to bearing Requirement on machining accuracy it is not high.

Embodiment nine

Figure 31 to Figure 38 is the structural schematic diagram of slot type gas magnetic hybrid radial bearing provided by the embodiment of the utility model.

As shown in Figure 31 to Figure 38, slot type gas magnetic hybrid radial bearing 6200 includes：

The 4th magnetic bearing 6201 being sheathed in shaft 100, it is circumferentially arranged on the 4th magnetic bearing 6201 to have multiple seven Magnetic part；

4th magnetic bearing 6201 towards shaft 100 side wall or shaft 100 towards on the periphery of the 4th magnetic bearing 6201 It is provided with third dynamic pressure generation trough 6202；

Wherein, there is the 4th gap 6203, and shaft 100 can be multiple between the 4th magnetic bearing 6201 and shaft 100 Moving in the radial direction in shaft 100 under the magneticaction of 7th magnetic part.

In the utility model embodiment, by the way that the 4th gap 6203 and the 4th magnetic bearing are arranged in transverse bearing 6200 6201, so that the transverse bearing 6200 be made to form gas, magnetic hybrid radial bearing.

When work, the gas bearing in transverse bearing 6200 can cooperate with the 4th magnetic bearing 6201, in radial axle When holding 6200 in stable working condition, realizes and support by gas bearing；And it is in non-stable in transverse bearing 6200 When working condition, transverse bearing 6200 is controlled and responded in time by the 4th magnetic bearing 6201.

In the utility model embodiment, when shaft 100 rotates, the flowing gas for being present in the 4th gap 6203 is pressed into In third dynamic pressure generation trough 6202, to generate pressure, shaft 100 is set to float, to realize that shaft 100 is radially connect by non- It contacts to earth holding.Wherein, third dynamic pressure generation trough 6202 generates angle of the size with third dynamic pressure generation trough 6202 of pressure, slot Width, flute length, groove depth, the difference of slot number and flatness and change.In addition, third dynamic pressure generation trough 6202 generates the size of pressure Also related with the rotation speed of shaft 100 and the 4th gap 6203.It can be according to actual condition to third dynamic pressure generation trough 6202 parameter is designed.Third dynamic pressure generation trough 6202 can be formed in by modes such as forging, rolling, etching or punching presses On 4th magnetic bearing 6201 or shaft.

Optionally, multiple 7th magnetic parts include multiple 4th permanent magnets, and multiple 4th permanent magnets are in the 4th magnetic bearing It is circumferentially arranged on 6201；

Alternatively, multiple 7th magnetic parts include multiple 4th electromagnet, multiple 4th electromagnet are in the 4th magnetic bearing Circumferentially arranged on 6201, the 4th electromagnet of each of multiple 4th electromagnet includes being set on the 4th magnetic bearing 6201 4th magnetic core 62011 and the 4th coil 62012 being wound on the 4th magnetic core 62011.

In the utility model embodiment, when slot type gas magnetic hybrid radial bearing 6200 only need magnetic part provide magnetic force and When without magnetic control, the 7th magnetic part preferably the 4th permanent magnet；When paillon formula gas magnetic mixing thrust bearing simultaneously need magnetic force and When magnetic control, the 7th magnetic part preferably the 4th electromagnet.

When the 7th magnetic part is four electromagnet, electric current is passed through toward the 4th coil 62012, it can make the 4th magnetic core 62011 generate magnetic force.The of different sizes of electric current, the magnetic force size that the 4th magnetic core 62011 generates are passed through toward the 4th coil 62012 It is different；It is passed through sense of current difference toward the 4th coil 62012, the magnetic pole of the 4th magnetic core 62011 is also different.

Wherein, since silicon steel sheet or silicon steel sheet have the physical characteristics such as magnetic conductivity is high, eddy-current loss is low, the utility model In preferred embodiment, the 4th magnetic core 62011 can be overrided to form by several silicon steel sheets or silicon steel sheet.

Optionally, the 4th magnetic bearing 6201 includes：

4th magnetic bearing seat 62013, the 4th magnetic bearing seat 62013 are sheathed in shaft 100, the 4th magnetic bearing seat 62013 Above circumferentially arranged to have multiple 4th holding tanks 62014, multiple 7th magnetic parts are set to multiple 4th holding tanks 62014 It is interior, and the magnetic pole of multiple 7th magnetic parts is towards shaft 100；

The second bearing shell 62015 being sheathed on outside the 4th magnetic bearing seat 62013；

The second bearing set 62016 being sheathed between the 4th magnetic bearing seat 62013 and shaft 100；

And it is respectively arranged at the 5th end cap 62017 and the 6th end cap 62018 at 62015 both ends of second bearing shell；

Wherein, second bearing covers the 62016, the 5th end cap 62017 and the cooperation of the 6th end cap 62018, magnetic by multiple seven Component is fixed on the 4th magnetic bearing seat 62013.

In the utility model embodiment, by setting second bearing cover 62016, can close the 4th magnetic core 62011 and Gap between 4th coil 62012, to form stable, uniform air film between second bearing set 62016 and shaft 100 Pressure.In addition, can be conveniently adjusted and control the 4th gap by the second bearing set 62016 that different radial thickness are arranged 6203 size.

Wherein, the width in the 4th gap 6203 between second bearing set 62016 and shaft 100 can be 5 μm to 12 μm, It is preferred that 8 μm to 10 μm.

Wherein, since silicon steel sheet or silicon steel sheet have the physical characteristics such as magnetic conductivity is high, eddy-current loss is low, the utility model In preferred embodiment, the 4th magnetic bearing seat 62013 can be overrided to form by several silicon steel sheets or silicon steel sheet.4th holding tank 62014 quantity can be but be not limited to six or eight, and the circumferential direction along the 4th magnetic bearing seat 62013 is uniformly arranged.In this way, The magnetic force between the 4th magnetic bearing 6201 and shaft 100 can be made more uniform, stable.It should be noted that multiple 7th magnetic Property component can also be set on the 4th magnetic bearing seat 62013 using other modes, to this without limiting.5th end cap 62017 and the 6th the material of end cap 62018 may each be non-magnetic material, preferably duralumin material.Second bearing set 62016 Material can be non-magnetic material, preferably duralumin material.The material of second bearing shell 62015 can be non-magnetic material, preferably Duralumin material.

Preferably, the 5th end cap 62017 and the 6th end cap 62018 are provided with the interior of outer diameter and second bearing shell 62015 The boss of the identical boss of diameter, the 5th end cap 62017 and the 6th end cap 62018 is for fixing and compressing the 4th magnetic of composition from both ends The silicon steel sheet or silicon steel sheet of bearing block 62013.

In the utility model embodiment, it can be covered in second bearing and third dynamic pressure generation trough 6202 is set on 62016, for just In the processing of third dynamic pressure generation trough 6202, second bearing set 62016 can be made of stainless steel material.Specifically, third is dynamic The middle section that the periphery of second bearing set 62016 is corresponded in shaft 100 can be set in pressure generation trough 6202, can also set It is set to the two sides for being symmetrically distributed in middle section, mutually independent two parts third dynamic pressure generation trough 6202；Third dynamic pressure occurs The middle section that second bearing covers 62016 inner sidewalls can also be arranged in slot 6202, may be set to be and be symmetrically distributed in second 62016 inner sidewall both ends of bearing holder (housing, cover), mutually independent two parts third dynamic pressure generation trough 6202.

Optionally, third dynamic pressure generation trough 6202 is arranged in matrix, in this way, being conducive to make air film to be more evenly distributed in the In four gaps 6203.

Optionally, third dynamic pressure generation trough 6202 is continuous or spaced V-shaped groove.

In the utility model embodiment, by using the set-up mode of above-mentioned third dynamic pressure generation trough 6202, it can turn In the case that axis 100 is rotated in the forward direction or reversely rotated, shaft can be kept in a non-contact manner in the desired manner, to make Shaft 100 has the advantages that high load capacity and stability are good.Third dynamic pressure generation trough 6202 may be used also in addition to being set as V-shaped groove To be set as man type chute or other shapes of slot.

Optionally, the second static pressure air inlet restriction hole 6205, the second static pressure air inlet section are additionally provided on the 4th magnetic bearing 6201 One end of discharge orifice 6205 is communicated with the 4th gap 6203, and the other end connects external air source, for external air source to be delivered to the 4th In gap 6203.

In the utility model embodiment, by the way that above-mentioned second static pressure air inlet restriction hole 6205 is arranged, it is quiet gas can be formed Last item is held, so that the slot type gas magnetic hybrid radial bearing 6200 may be constructed slot type gas dynamic and static pressure-magnetic hybrid radial bearing.Its In, the circulation diameter in the second static pressure air inlet restriction hole 6205 can be adjusted according to actual conditions such as tolerance demands.

Optionally, the second static pressure air inlet restriction hole 6205 is divided at least two branches in the 4th magnetic bearing 6201 and is connected to In 4th gap 6203.

In the utility model embodiment, the second static pressure air inlet restriction hole 6205 can sequentially pass through the 5th end cap 62017 or 6th end cap 62018, the 4th magnetic bearing 6201 and second bearing set 62016, external air source is connected to the 4th gap 6203. Further, the second static pressure air inlet restriction hole 6205 can be divided into two or more branch and be connected to the 4th gap 6203, So that the gas film pressure in the 4th gap 6203 is more uniform.Further, on the 5th end cap 62017 or the 6th end cap 62018 Annular groove can be set, multiple second static pressure can be set in the 4th magnetic bearing 6201 annular region corresponding with the annular groove Air inlet restriction hole 6205, for example, being arranged one in each 4th magnetic core 62011 or in every two adjacent 4th magnetic core 62011 A second static pressure air inlet restriction hole 6205.Wherein, the circulation diameter of the second static pressure air inlet restriction hole 6205 and branch can root It is adjusted according to actual conditions such as tolerance demands.

Optionally, slot type gas magnetic hybrid radial bearing 6200 further includes along the circumferentially spaced of the 4th magnetic bearing 6201 Multiple 4th sensors 6204, wherein the sensor probe of each 4th sensor 6204 is set in the 4th gap 6203.

It, can be at the 4th gap 6203 of real-time detection by the way that the 4th sensor 6204 is arranged in the utility model embodiment Parameter, such as the gas film pressure at the 4th gap 6203.In this way, the 4th magnetic bearing 6201 can be according to the 4th sensor 6204 Testing result to transverse bearing 6200 carry out active control, and can make control reach higher precision.

Optionally, in multiple 4th sensors 6204, each 4th sensor 6204 includes 62041 He of the 4th sender unit cap 4th sensor probe 62042, the first end of the 4th sensor probe 62042 connect the 4th sender unit cap 62041, the 4th sensing Device lid 62041 is fixed on the 4th magnetic bearing 6201, and the 4th magnetic bearing 6201 is equipped with for supplying the 4th sensor probe 62042 through-holes passed through；The second end of 4th sensor probe 62042 passes through the through-hole on the 4th magnetic bearing 6201, and extends to 4th gap 6203, and the close shaft 100 of the second end end of the 4th sensor probe 62042 and the 4th magnetic bearing 6201 Side it is concordant.

In the utility model embodiment, by the structure type and mounting means of above-mentioned 4th sensor 6204, it can make 4th sensor 6204 is more stably set on the 4th magnetic bearing 6201.In addition, by the second of the 4th sensor probe 62042 Hold end concordant with the side of close shaft 100 of the 4th magnetic bearing 6201, on the one hand, to can be avoided the 4th sensor probe 62042 are touched by shaft 100, to be conducive to protect the 4th sensor probe 62042；It on the other hand, will not be to the 4th Air film in gap 6203 has an impact, and the air film in the 4th gap 6203 is avoided to disturb.

Optionally, in multiple 4th sensors 6204, each 4th sensor 6204 is respectively arranged at adjacent two Between seven magnetic parts.

In the utility model embodiment, the quantity of the 4th sensor 6204 can be identical as the quantity of the 7th magnetic part. 4th sensor 6204 can be set between two adjacent the 7th magnetic parts, can also pass through the 7th magnetic part and set It sets, the utility model embodiment is not construed as limiting this.Each 4th sensor 6204 is preferably disposed on the 4th magnetic bearing 6201 Middle part.

Optionally, multiple 4th sensors 6204 are any one or more following combination：

For detecting the displacement sensor of 100 position of shaft；

For detecting the pressure sensor of the gas film pressure at the 4th gap 6203；

For detecting the velocity sensor of 100 revolving speed of shaft；

For detecting the acceleration transducer of 100 rotary acceleration of shaft.

Below with slot type gas magnetic hybrid radial bearing (wherein, the 7th in the 4th magnetic bearing of the utility model embodiment Magnetic part is electromagnet) participate in rotor-support-foundation system control process when specific control method be described in detail.

The utility model embodiment provides a kind of control method of slot type gas magnetic hybrid radial bearing, including：

S631, the 4th magnetic bearing is opened, controls the shaft in the magneticaction of the multiple 7th magnetic part Under moving in the radial direction in the shaft, push the shaft to preset radial position.

S632, shaft revolving speed accelerate to after working speed, close the 4th magnetic bearing.

When S633, rotor-support-foundation system are shut down, the 4th magnetic bearing is opened.

S634, shaft revolving speed be decelerated to after zero, close the 4th magnetic bearing.

In above process, after the 4th magnetic bearing is opened, shaft holds up and reaches default under the action of four magnetic bearings Radial position has the 4th gap between the 4th magnetic bearing and shaft.

With the rotation of shaft, shaft starts turning in the case that air-flow lubricates in by the 4th gap, to prevent from wearing. 4th magnetic bearing open detailed process be：To the current signal of the 4th coil input predetermined value, shaft is in the 4th magnetic bearing It is held up under effect and reaches preset radial position.

As the revolving speed of shaft is increasing, when the revolving speed of shaft reaches working speed, the gas of the transverse bearing is dynamic Last item holds and (aero dynamic bearing that the 4th gap forms the transverse bearing is arranged between the 4th magnetic bearing and shaft) generation Gas film pressure can stablize shaft, can close the 4th magnetic bearing at that time.

When rotor-support-foundation system is shut down, shaft is slowed down, in order to make shaft keep stablizing in entire rotor-support-foundation system stopping process, The 4th magnetic bearing is opened when rotor-support-foundation system is shut down, and the 4th magnetic bearing can be closed after shaft is stopped completely.

The utility model embodiment also provides the control method of another slot type gas magnetic hybrid radial bearing, including：

S641, the 4th magnetic bearing is opened, controls the shaft in the magneticaction of the multiple 7th magnetic part Under moving in the radial direction in the shaft, push the shaft to preset radial position.

S642, shaft revolving speed accelerate to after the first preset value, close the 4th magnetic bearing.

Revolving speed when accelerating to single order critical speed or the second order critical speed of S643, shaft, open the 4th magnetic bearing.

Specifically, when the gas flow rate of the 4th gap location between shaft and the 4th magnetic bearing reach single order critical speed or When second order critical speed, the 4th magnetic bearing is opened, until shaft is restored to balance radial position.

Optionally, when the revolving speed of shaft accelerates to single order critical speed or the second order critical speed, the 4th magnetic axis is opened It holds, including：

When the revolving speed of shaft accelerates to single order critical speed or the second order critical speed, the 4th magnetic bearing is controlled with maximum Power is opened；Alternatively,

When the revolving speed of shaft accelerates to single order critical speed or the second order critical speed, the 4th magnetic bearing is controlled according to pre- If frequency is opened in a manner of stroboscopic.

S644, rotor-support-foundation system are steadily spent after single order critical speed or the second order critical speed, and the 4th magnetic axis is closed It holds.

In S645, rotor-support-foundation system stopping process, when the rotor-support-foundation system is decelerated to the single order critical speed or described two When rank critical speed, the 4th magnetic bearing is opened.

Specifically, when the gas flow rate of the 4th gap location between shaft and the 4th magnetic bearing is decelerated to single order critical speed Or when second order critical speed, the 4th magnetic bearing is opened, until shaft is restored to balance radial position.

Optionally, when the revolving speed of shaft is decelerated to single order critical speed or the second order critical speed, the 4th magnetic axis is opened It holds, including：

When the revolving speed of shaft is decelerated to single order critical speed or the second order critical speed, the 4th magnetic bearing is controlled with maximum Power is opened；Alternatively,

When the revolving speed of shaft is decelerated to single order critical speed or the second order critical speed, the 4th magnetic bearing is controlled according to pre- If frequency is opened in a manner of stroboscopic.

S646, rotor-support-foundation system are steadily spent after the single order critical speed or the second order critical speed, close the 4th Magnetic bearing.

Revolving speed when being decelerated to the second preset value of S647, shaft, open the 4th magnetic bearing.

S648, the shaft revolving speed be decelerated to after zero, close the 4th magnetic bearing.

As the revolving speed of shaft is increasing, when shaft revolving speed reach the first preset value, such as rated speed 5% to When 30%, the aero dynamic bearing of the transverse bearing (is arranged the 4th gap and forms the radial direction between the 4th magnetic bearing and shaft The aero dynamic bearing of bearing) generate gas film pressure can by shaft stablize, the 4th magnetic bearing can be closed at that time.

In rotor-support-foundation system stopping process, shaft is slowed down, when the revolving speed of shaft is down to the second preset value, such as rated speed 5% to 30% when, open the 4th magnetic bearing, the 4th magnetic bearing can be closed after shaft is stopped completely.

Optionally, the method also includes：

When the 4th gap between the shaft and the 4th magnetic bearing changes, the 4th magnetic axis is opened Hold, make the shaft under the magneticaction of the multiple 7th magnetic part to far from gap become smaller side direction it is mobile；

The shaft is in after balance radial position, closes the 4th magnetic bearing.

When load is supported in shaft, it is gradually reduced shaft and when close to four magnetic bearing of lower section, the 4th sensor (the 4th preferred pressure sensor of sensor here) obtains the signal that air pressure increases, and the 4th magnetic bearing needs to intervene work at this time Make.4th magnetic bearing by magneticaction in making it suspend in shaft upwards, when shaft reaches new equilbrium position, the 4th magnetic axis It holds and stops working.

When there is external impact disturbance to occur, shaft may be rapidly close to the 4th magnetic bearing, it is likely that leads to shaft Gap moment between the 4th magnetic bearing is too small, makes the close even up to velocity of sound of the local gas flow velocity at the reduction of gap, from And causes shock wave and generate Pneumatic hammer phenomenon.The generation of shock wave will lead to local gas flow and disturbance and confusion occur, and work as fluid Speed is remarkably decreased in velocity of sound to its pressure when changing between subsonic speed in staged.In this case, it needs to control the 4th magnetic 7th magnetic part of bearing is opened in turn with predeterminated frequency, to provide the damping action to disturbance, to effectively inhibit external Disturbance.When shaft is restored to after new balance radial position, the 4th magnetic bearing stops working.

It should be noted that in the utility model embodiment, for being provided with electromagnetic bearing (in the 4th magnetic bearing simultaneously 7th magnetic part is that electromagnet forms electromagnetic bearing) and aerostatic bearing (the second static pressure being arranged on the 4th magnetic bearing Air inlet restriction hole forms aerostatic bearing) in the case where, electromagnetic bearing and aerostatic bearing can be mutually spare, at it In side's failure, fail or be unable to satisfy unlocking condition in the case where, another party can be used as replacement bearing and play identical work With.For example, control external air source is opened to substitute electromagnetic bearing and execute accordingly in the case where detecting electromagnetic bearing failure Movement, to improve the safety and reliability of bearing.

It, can be in the case where being provided with electromagnetic bearing and aerostatic bearing simultaneously in the utility model embodiment Including mode is implemented as follows：

Open the 4th magnetic bearing；And/or starting external air source, by the second static pressure air inlet restriction hole to the 4th gap location Convey gas；

The shaft is controlled under the magneticaction of multiple 7th magnetic parts and/or under the impetus of the gas In moving in the radial direction for the shaft, so that the shaft is moved to preset radial position.

Wherein, for the embodiment of the 4th magnetic bearing and aerostatic bearing of unlatching simultaneously, this can be further increased The bearing capacity of the transverse bearing of utility model embodiment.

In above process, the advantages of facilitating real-time control using the 4th magnetic bearing, the uneven matter of active balancing shaft Amount or shaft whirling motion etc. lead to the factor of shaft over-deflection, are fixed on shaft in radial directions in a certain very low range. In addition, the position (i.e. linear velocity supersonic speed position) for generating shock wave can be accurately positioned, and pass through in the accelerator of shaft Size of current and the direction etc. for controlling the 4th magnetic bearing, make the 4th magnetic bearing generate opposite power to balance Shock Wave.Wait swash After popin is steady, the control strategy of the 4th magnetic bearing is adjusted again, and shaft is fixed on a certain very low range in a manner of most energy-efficient It is interior.

In summary, the utility model embodiment has the advantages that：

First, electromagnetic bearing and gas bearing cooperate, dynamic property of the bearing under the state of running at high speed is improved And stability, resist disturbed kinetic force strong, and then improve the bearing capacity of bearing.Meanwhile electromagnetic bearing and gas bearing use Nested structure simplifies structure, and integrated level is high, and easy processing, manufacture and operation improve the comprehensive performance of bearing.In rotor system When system starting or shutdown, the thrust disc of bearing and stator can be made to rotate in the first gap with electromagnetic bearing, improve bearing Low-speed performance, extend the service life of bearing, can be improved the safety and reliability of bearing and whole system.

Second, being pushed away relative to traditional gas hybrid combined using aerostatic bearing and aero dynamic bearing The slot type gas magnetic hybrid radial bearing of power bearing, the utility model embodiment has the advantages that fast response time.

Third, increasing aerostatic bearing, slot type dynamic and static pressure-magnetic mixing thrust bearing is formed, is provided with electricity at the same time In the case where magnetic bearing and aerostatic bearing, the bearing capacity of bearing is further increased, and electromagnetic bearing and aerostatic bearing can With mutually spare, in the case where wherein side's failure, failing or being unable to satisfy unlocking condition, another party can be used as immobilized spindle It holds and serves the same role.For example, control system controls aerostatic bearing and opens the case where detecting electromagnetic bearing failure Corresponding movement is executed to substitute electromagnetic bearing, to improve the safety and reliability of bearing.

More than, only specific embodiment of the present utility model, but protection scope of the utility model is not limited thereto, Anyone skilled in the art within the technical scope disclosed by the utility model, can readily occur in variation or replace It changes, should be covered within the scope of the utility model.Therefore, the protection scope of the utility model should be with claim Subject to protection scope.

Claims

1. a kind of bearing, for being installed on shaft, which is characterized in that the bearing includes：

The sub- bearing of radial direction being set in first accommodating chamber, the sub- bearing of radial direction are arranged in the shaft, the diameter To between sub- bearing and the shaft have the first gap；

And it is set to the sub- bearing of thrust in second accommodating chamber, the sub- bearing of thrust includes thrust disc, and respectively It is set to the first stator and the second stator of the thrust disc two sides, the thrust disc is fixedly connected in the shaft, described First stator and second stator are arranged in the shaft；In first stator and second stator, Mei Geding It is sub that there is the second gap between the thrust disc.

2. bearing according to claim 1, which is characterized in that

The sub- bearing of radial direction includes the first magnetic bearing being sheathed in the shaft, first magnetic bearing and the shaft it Between there is first gap, it is circumferentially arranged on first magnetic bearing to have multiple first magnetic parts；The shaft can The moving in the radial direction in the shaft under the magneticaction of the multiple first magnetic part；

In first stator and second stator, each stator includes the second magnetic bearing, along week on second magnetic bearing To being provided with multiple second magnetic parts；Third magnetic part is provided on the thrust disc, the thrust disc can be described It is moved on the axial direction of the shaft under magneticaction between multiple second magnetic parts and the third magnetic part.

3. bearing according to claim 2, which is characterized in that

First magnetic bearing includes：

First magnetic bearing seat, the first magnetic bearing cover for seat are set in the shaft, circumferentially set on the first magnetic bearing seat Multiple first holding tanks are equipped with, the multiple first magnetic part is set in the multiple first holding tank, and the multiple The magnetic pole of first magnetic part is towards the shaft；

And be sheathed on the bearing holder (housing, cover) between the first magnetic bearing seat and the shaft, the bearing holder (housing, cover) and the shaft it Between there is first gap, the bearing holder (housing, cover) and the first magnetic bearing seat cooperate, the multiple first magnetic part are consolidated Due on the first magnetic bearing seat.

4. bearing according to claim 2, which is characterized in that

The multiple first magnetic part includes multiple first permanent magnets, and the multiple first permanent magnet is in first magnetic bearing It is upper circumferentially arranged；

Alternatively, the multiple first magnetic part includes multiple first electromagnet, the multiple first electromagnet is described first Circumferentially arranged on magnetic bearing, the first electromagnet of each of the multiple first electromagnet includes being set to first magnetic axis The first magnetic core held and the first coil being wound on first magnetic core.

5. bearing according to claim 2, which is characterized in that

First magnetic bearing is arranged towards the side wall of the shaft or the periphery of the shaft towards first magnetic bearing There is the first dynamic pressure generation trough.

6. bearing according to claim 2, which is characterized in that

The sub- bearing of radial direction further includes circumferentially spaced multiple first sensors along first magnetic bearing, described more A first sensor is any one or more following combination：

For detecting the displacement sensor of the rotating shaft position；

For detecting the velocity sensor of the shaft revolving speed；

For detecting the acceleration transducer of the shaft rotary acceleration.

7. bearing according to claim 6, which is characterized in that

In the multiple first sensor, each first sensor includes passing the first sensor lid and first sensor probe, described The first end of first sensor probe connects the first sensor lid, and the first sensor lid is fixed on first magnetic axis Hold, first magnetic bearing be equipped with for for the first sensor probe across through-hole；The first sensor is visited The second end of head passes through the through-hole on first magnetic bearing, and extends to first gap, and the first sensor is popped one's head in Second end end and first magnetic bearing it is concordant close to the side of the shaft.

8. bearing according to claim 2, which is characterized in that

Second magnetic bearing includes：

Second magnetic bearing seat, the second magnetic bearing seat are oppositely arranged with the thrust disc, along week on the second magnetic bearing seat To multiple second holding tanks are provided with, the multiple second magnetic part is set in the multiple second holding tank, and described Side where the magnetic pole towards the thrust disc of multiple second magnetic parts；

Pressure ring, the pressure ring be set to the second magnetic bearing seat close to the thrust disc side, the pressure ring with it is described The cooperation of second magnetic bearing seat, the multiple second magnetic part is fixed on the second magnetic bearing seat.

9. bearing according to claim 2, which is characterized in that

The multiple second magnetic part includes multiple second permanent magnets, and the multiple second permanent magnet is in second magnetic bearing It is upper circumferentially arranged；

Alternatively, the multiple second magnetic part includes multiple second electromagnet, the multiple second electromagnet is described second Circumferentially arranged on magnetic bearing, the second electromagnet of each of the multiple second electromagnet includes being set to second magnetic axis The second magnetic core held and the second coil being wound on second magnetic core.

10. bearing according to claim 2, which is characterized in that

The third magnetic part includes the end towards first stator and second stator for being set to the thrust disc Magnetic material on face；

Wherein, magnetic material distribution in a strip shape on the thrust disc, and multiple strip magnetic portions are formed, the multiple item Shape magnetic portion is radially or circumferentially；

11. bearing according to claim 2, which is characterized in that

The end face towards first stator and second stator of the thrust disc, or, first stator and described The second dynamic pressure generation trough is provided on the end face towards the thrust disc of two stators.

12. bearing according to claim 11, which is characterized in that

The second dynamic pressure generation trough is radially or concentric circles are arranged.

13. bearing according to claim 12, which is characterized in that

The second dynamic pressure generation trough includes the first spiral groove and the second spiral groove, and first helicla flute is surrounded on described second Outside helicla flute, the spiral of first helicla flute and second helicla flute moves towards the close institute on the contrary, first helicla flute The one end for stating the second helicla flute and one end close to first helicla flute of second helicla flute connect or disconnect.

14. bearing according to claim 2, which is characterized in that

It is additionally provided with second sensor on the sub- bearing of thrust, the second sensor is any one or more following group It closes：

For detecting the displacement sensor of the thrust disc position；

For detecting the velocity sensor of the thrust disk rotating speed；

15. bearing according to claim 14, which is characterized in that

The second sensor includes second sensor lid and second sensor probe, the first end of the second sensor probe The second sensor lid is connected, the second sensor lid is fixed on second magnetic bearing, on second magnetic bearing Equipped with for for the second sensor probe across through-hole；The second end of the second sensor probe passes through described second Through-hole on magnetic bearing, and second gap is extended to, and the second end end and described second of second sensor probe The side close to the thrust disc of magnetic bearing is concordant.

16. bearing according to claim 2, which is characterized in that

The cartridge housing is additionally provided with static pressure air inlet restriction hole；

Wherein, the one end in static pressure air inlet restriction hole connects external air source, and the other end is through the sub- bearing of the radial direction and described the One gap communicates, and communicates through first stator and second stator with second gap, the static pressure air inlet restriction Hole is used to external air source being delivered to first gap and second gap.

17. a kind of rotor-support-foundation system, which is characterized in that

Including shaft and the thrust bearing and at least two transverse bearings that are set in the shaft, the thrust bearing and described At least two transverse bearings are non-contact type bearing；

The thrust bearing and the transverse bearing adjacent with the thrust bearing are integrated, are formed as in claim 2 to 15 Described in any item bearings.

18. rotor-support-foundation system according to claim 17, which is characterized in that

The axis body of the shaft is structure as a whole, and the shaft is horizontally disposed or vertically arranged；

Motor, compressor and turbine are disposed in the shaft；

Wherein, the thrust bearing is set on the predeterminated position of the side of the close compressor of the turbine, described pre- If position is two radial directions that the center of gravity of the rotor-support-foundation system can be made to be located at lie farthest away at least two transverse bearing Position between bearing.

19. rotor-support-foundation system according to claim 17, which is characterized in that

It is non-contact that motor, compressor, turbine and two transverse bearings, described two transverse bearings are provided in the shaft Formula bearing；

Wherein, the motor, the thrust bearing and described two transverse bearings are all set in first casing, the pressure Mechanism of qi and the turbine are all set in second casing, and the impeller of the impeller of the compressor and the turbine is described the Mutually by setting in two casings.