CN208236900U

CN208236900U - A kind of thrust bearing and rotor-support-foundation system

Info

Publication number: CN208236900U
Application number: CN201820845722.0U
Authority: CN
Inventors: 靳普
Original assignee: To Yue Teng Wind Technology Investment Group Ltd
Current assignee: Liu Muhua
Priority date: 2018-06-01
Filing date: 2018-06-01
Publication date: 2018-12-14
Anticipated expiration: 2028-06-01

Abstract

The utility model provides a kind of thrust bearing and rotor-support-foundation system, and wherein thrust bearing includes: thrust disc, and thrust disc is fixedly connected in shaft；And it is arranged in the first stator and the second stator in shaft, the opposite sides that the first stator and the second stator are respectively arranged at thrust disc has the second gap with the first gap between the first stator and thrust disc between the second stator and thrust disc；Wherein, the first stator includes magnetic bearing, and circumferentially arranged on magnetic bearing to have multiple first magnetic parts, magnetic bearing can control thrust disc and move on the axial direction of shaft；Gas bearing is constituted between second stator and thrust disc.Magnetic bearing and gas bearing is respectively set by the two sides in thrust bearing in the utility model, to make the thrust bearing form gas magnetic mixing thrust bearing, since gas bearing and magnetic bearing can cooperate, dynamic property and stability of the thrust bearing under the state of running at high speed can be improved.

Description

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

Technical field

The utility model relates to technical field of bearings more particularly to a kind of thrust 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 axial direction.In order to limit the movement in shaft generation axial direction, rotor Installed thrust bearing is needed in system.Traditional thrust bearing is common contact bearing, with the raising of rotor speed, Especially rotor speed per minute more than 40000 turns when, common contact bearing is since there are biggish mechanical wears, not It is able to satisfy the demand of working speed, this just needs to substitute contact bearing using non-contact type bearing.

In the prior art, non-contact type bearing generally comprises magnetic bearing and air bearing.However, magnetic bearing is opened for a long time When the problems such as there are energy consumption is too big and fever；And air bearing can be generated when linear resonance surface velocity is near or above velocity of sound Shock wave so as to cause bearing unstability, or even generates the catastrophic effects such as bar resets.As it can be seen that the equal nothing of both the above non-contact type bearing Method is suitable for high-revolving gas turbine or gas turbine power generation Unit erriger.

As it can be seen that it is urgent to provide the control methods of a kind of new thrust bearing, rotor-support-foundation system and thrust bearing at present, to solve The above problem.

Utility model content

The utility model provides a kind of thrust bearing and rotor-support-foundation system, to solve the above problems.

In a first aspect, the utility model provides a kind of thrust bearing, for being installed on shaft, the thrust axis is contracted It includes:

Thrust disc, the thrust disc are fixedly connected in the shaft；

And it is arranged in the first stator and the second stator in the shaft, first stator and second stator It is respectively arranged at the opposite sides of the thrust disc, there is the first gap between first stator and the thrust disc, it is described There is the second gap between second stator and the thrust disc；

Wherein, first stator includes magnetic bearing, circumferentially arranged on the magnetic bearing to have multiple first magnetic parts, The magnetic bearing can control the thrust disc and move on the axial direction of the shaft；Second stator and the thrust Gas bearing is constituted between disk.

Second aspect, the utility model provide a kind of rotor-support-foundation system, including thrust bearing described in shaft and first aspect.

In the utility model, by the way that magnetic bearing is arranged in the side of thrust bearing, gas bearing is arranged in the other side, to make The thrust bearing forms gas magnetic mixing thrust bearing.In this way, this is practical new since gas bearing and magnetic bearing can cooperate Type can improve thrust bearing, and dynamic property and stability especially under the state of running at high speed resist disturbed kinetic force strong, in turn Improve the bearing capacity of thrust bearing.As it can be seen that the thrust bearing of the utility model can satisfy high-revolving gas turbine or The demand of person's gas turbine power generation Unit erriger etc..

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 structural schematic diagram of thrust bearing provided by the embodiment of the utility model；

Fig. 2 is the structural schematic diagram of another thrust bearing provided by the embodiment of the utility model；

Fig. 3 is the structural schematic diagram of magnetic bearing in thrust bearing provided by the embodiment of the utility model；

Fig. 4 is the structural schematic diagram of magnetic bearing seat in thrust bearing provided by the embodiment of the utility model；

Fig. 5 is the structural schematic diagram of the first paillon in thrust bearing provided by the embodiment of the utility model；

Fig. 6 is one of the structural schematic diagram of dynamic pressure generation trough in thrust bearing provided by the embodiment of the utility model；

Fig. 7 is the second structural representation of dynamic pressure generation trough in thrust bearing provided by the embodiment of the utility model；

Fig. 8 is the third structural representation of dynamic pressure generation trough in thrust bearing provided by the embodiment of the utility model；

Fig. 9 is four of the structural schematic diagram of dynamic pressure generation trough in thrust bearing provided by the embodiment of the utility model；

Figure 10 to Figure 30 is the structural schematic diagram of rotor-support-foundation system provided by the embodiment of the utility model；

Figure 31 is a kind of flow diagram of the control method of thrust bearing provided by the embodiment of the utility model；

Figure 32 is the flow diagram of the control method of another thrust bearing provided by the embodiment of the utility model；

Figure 33 to Figure 40 is the structural schematic diagram of slot type gas magnetic hybrid radial bearing provided by the embodiment of the utility model.

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 9, the utility model embodiment provides a kind of thrust bearing, for being installed on shaft 100, Thrust bearing includes:

Thrust disc 701, thrust disc 701 are fixedly connected in shaft 100；

And it is arranged in the first stator 702 and the second stator 703 in shaft 100, the first stator 702 and the second stator 703 are respectively arranged at the opposite sides of thrust disc 701, between the first stator 702 and thrust disc 701 have the first gap, second There is the second gap between stator 703 and thrust disc 701；

Wherein, the first stator 702 includes magnetic bearing 704, circumferentially arranged on magnetic bearing 704 to have multiple first magnetic portions Part, magnetic bearing 704 can control thrust disc 701 and move on the axial direction of shaft 100；Second stator 703 and thrust disc 701 Between constitute gas bearing.

In the utility model embodiment, by the way that the first gap is arranged between the first stator 702 and thrust disc 701, and Magnetic bearing 704 is set in the first stator 702, so that the side forms magnetic bearing；By the second stator 703 and thrust disc 701 it Between the second gap is set so that the side formed gas bearing so that thrust bearing formed gas magnetic mixing thrust bearing.

When work, the magnetic bearing 704 in thrust bearing can cooperate with gas bearing, be in and stablize in thrust bearing Working condition when, by gas bearing realize support；And when thrust bearing is in non-stable working condition, by magnetic axis 704 are held thrust bearing is controlled and responded in time.

As it can be seen that the utility model embodiment can improve thrust bearing under the state of running at high speed by above-mentioned setting Dynamic property and stability resist disturbed kinetic force strong, and then improve the bearing capacity of thrust bearing.Shaft 100 starting or When shutdown, dynamic pressure air film is not yet established or is disappeared, and is rotated thrust disc 701 and stator in scheduled gap with magnetic bearing 704, is mentioned The high low-speed performance of gas bearing, reduces the negative effect of thrust disc 701 vibration and impact, extends the use of thrust bearing Service life improves the reliability of whole system.Due to the above-mentioned characteristic of thrust bearing, the thrust bearing of the utility model embodiment It can satisfy the demand of high-revolving gas turbine or gas turbine power generation Unit erriger etc..

In the utility model embodiment, magnetic bearing 704 and gas bearing are respectively arranged to the two sides of thrust disc 701, phase Than for the case where 701 two sides of thrust disc are gas magnetic combined bearing, the utility model embodiment not only can achieve identical Technical effect, also there are other advantages.On the one hand, do not have to take into account between gas bearing pair when magnetic bearing 704 is processed in design The strict demand of gap, when designing processing gas bearing without the structural requirement for taking into account magnetic bearing 704, therefore, by magnetic bearing 704 and gas bearing be provided separately, structure is simpler, it is easier to process and manufacture.On the other hand, magnetic axis only is set in side 704 are held, low energy consumption.In addition, 704 independent control of gas bearing and magnetic bearing, is independent of each other, improves the reliable of bearing control Property.

In the utility model embodiment, the outer diameter of thrust disc 701, the first stator 702 and the second stator 703 can be equal, When the thrust bearing of the utility model embodiment is applied to gas turbine or gas turbine power generation Unit erriger, the first stator 702 and second stator 703 can be connected by the shell of connector and gas turbine.

Optionally, the second magnetic part is provided on thrust disc 701, thrust disc 701 can be in multiple first magnetic parts And it is moved on the axial direction of shaft 100 under the second magneticaction between magnetic part.Second magnetic part includes setting Magnetic material on the end face towards the first stator 702 of thrust disc 701；Wherein, magnetic material is in item on thrust disc 701 Shape distribution, and multiple strip magnetic portions are formed, multiple strip magnetic portions are radially or circumferentially；Alternatively, magnetic material is in thrust It is in spot distribution on disk 701.

In the utility model embodiment, make magnetic material distribution in a strip shape or spot distribution on thrust disc 701, it can will The magnetic force generated between first magnetic part and the second magnetic part is controlled in reasonable range.

Optionally, magnetic bearing 704 includes:

Magnetic bearing seat 7043, magnetic bearing seat 7043 are oppositely arranged with thrust disc 701, circumferentially arranged on magnetic bearing seat 7043 There are multiple holding tanks, multiple first magnetic parts are set in multiple holding tanks, and the magnetic pole direction of multiple first magnetic parts Side where thrust disc 701；

End cap 707 and pressure ring 709, end cap 707 are set to the side of the separate thrust disc 701 of magnetic bearing seat 7043, pressure ring 709 are set to the side of the close thrust disc 701 of magnetic bearing seat 7043, and end cap 707 and pressure ring 709 cooperate, by multiple first magnetic Property component is fixed on magnetic bearing seat 7043.

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, magnetic bearing seat 7043 is overrided to form by several silicon steel sheets or silicon steel sheet.The quantity of holding tank can be but Six or eight are not limited to, the circumferential direction along magnetic bearing seat 7043 is uniformly arranged.In such manner, it is possible to make magnetic bearing 704 and thrust disc Magnetic force between 701 is more uniform, stable.It should be noted that multiple first magnetic parts can also be set using other modes It is placed on magnetic bearing seat 7043, to this without limiting.The material of end cap 707 can be non-magnetic material, preferably duralumin material. The material of pressure ring 709 can be non-magnetic material, preferably duralumin material.

Optionally, multiple first magnetic parts include multiple permanent magnets, and multiple permanent magnets are circumferentially set on magnetic bearing 704 It sets；Alternatively, multiple first magnetic parts include multiple electromagnet, multiple electromagnet are circumferentially arranged on magnetic bearing 704, multiple Each electromagnet in electromagnet includes the magnetic core 7041 being set on magnetic bearing 704 and the coil being wound on magnetic core 7041 7042。

In the utility model embodiment, when thrust bearing only needs the second magnetic part to provide magnetic force without magnetic control, The preferred permanent magnet of second magnetic part；When thrust bearing needs the second magnetic part to provide magnetic force and magnetic control simultaneously, the second magnetic The property preferred electromagnet of component.

When the second magnetic part is electromagnet, electric current is passed through toward coil 7042, it can magnetic core 7041 is made to generate magnetic force. It is passed through the of different sizes of electric current toward coil 7042, the magnetic force size that magnetic core 7041 generates is also different；Electric current is passed through toward coil 7042 Direction it is different, the magnetic pole of magnetic core 7041 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, magnetic core 7041 is overrided to form by several silicon steel sheets or silicon steel sheet.

Optionally, the first stator 702 is provided with sensor 7081, and sensor 7081 includes that sender unit cap and sensor are visited The first end of head, sensor probe connects sender unit cap, and sender unit cap is fixed on magnetic bearing 704, and the second of sensor probe End is across magnetic bearing 704 and extends to the first gap；And/or

Second stator 703 is provided with sensor 7081, and sensor 7081 includes sender unit cap and sensor probe, sensor The first end of probe connects sender unit cap, and sender unit cap is fixed on the second stator 703, and the second end of sensor probe passes through the Two stators 703 simultaneously extend to the second gap.

In the utility model embodiment, by the way that sensor is arranged, it is capable of the first gap of real-time detection or the second gap location Parameter, such as gas film pressure etc..In this way, magnetic bearing 704 can carry out actively thrust bearing according to the testing result of sensor Control, and control can be made to reach higher precision.

Optionally, in the case where the gas magnetic combined bearing of thrust bearing is slot type gas magnetic combined bearing, on magnetic bearing 704 Equipped with the through-hole 7082 for being passed through for sensor probe；The second end of sensor probe passes through the through-hole on magnetic bearing 704 7082, and the second end end of sensor probe is concordant with the side of close thrust disc 701 of magnetic bearing 704.

In this way, passing through the structure type and mounting means of the sensor 7081, sensor 7081 can be made more stably It is set on magnetic bearing 704.In addition, by the second end end of sensor probe and the one of the close thrust disc 701 of magnetic bearing 704 Side is concordantly arranged, on the one hand, can be avoided sensor probe and is touched by thrust disc 701, to be conducive to protect sensor Probe；On the other hand, the air film in the first gap will not be had an impact, the air film in the first gap is avoided to disturb.

Optionally, sensor 7081 is set between two adjacent the second magnetic parts.

Optionally, in the case where the gas magnetic combined bearing of thrust bearing is paillon formula gas magnetic combined bearing, magnetic bearing 704 The through-hole 7082 for passing through for sensor probe is equipped with foil bearing 705；The second end of sensor probe passes through magnetic axis The through-hole 7082 on 704 and foil bearing 705 is held, and the second end end of sensor probe is pushed away with the close of foil bearing 705 The side of power disk 701 is concordant.

In this way, passing through the structure type and mounting means of the sensor 7081, sensor 7081 can be made more stably It is set on magnetic bearing 704.In addition, by the close thrust disc 701 of the second end end of sensor probe and foil bearing 705 Side is concordant, on the one hand, can be avoided sensor probe and is touched by thrust disc 701, to be conducive to that sensor is protected to visit Head；On the other hand, the air film in the first gap will not be had an impact, the air film in the first gap is avoided to disturb.

Optionally, the second stator 703 is equipped with the through-hole for passing through for sensor probe；The second end of sensor probe Through-hole on the second stator 703, and the close thrust disc 701 of the second end end of sensor probe and the second stator 703 Side it is concordant.

In this way, passing through the structure type and mounting means of the sensor 7081, sensor 7081 can be made more stably It is set on the second stator 703.In addition, by the close thrust disc 701 of the second end end of sensor probe and the second stator 703 Side be concordantly arranged, on the one hand, can be avoided sensor probe and touched by thrust disc 701, thus be conducive to protection pass Sensor probe；On the other hand, the air film in the second gap will not be had an impact, the air film in the second gap is avoided to disturb It is dynamic.

Optionally, the sensor 7081 of the first stator 702 setting is any one or more following combination:

For detecting the displacement sensor of 701 position of thrust disc；

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

For detecting the velocity sensor of 701 revolving speed of thrust disc；

For detecting the acceleration transducer of 701 rotary acceleration of thrust disc.

Optionally, the sensor 7081 of the second stator 703 setting is any one or more following combination:

For detecting the displacement sensor of 701 position of thrust disc；

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

For detecting the velocity sensor of 701 revolving speed of thrust disc；

In the utility model embodiment, the side of the magnetic bearing of thrust bearing can be the pure magnetic axis of above structure form It holds, or gas magnetic combined bearing.And the gas magnetic combined bearing can be the slot type gas magnetic mixing axis including above-mentioned magnetic bearing It holds, can also be the paillon formula gas magnetic combined bearing including above-mentioned magnetic bearing, below for the various implementations of gas magnetic combined bearing Mode is described one by one.

On the one hand, being with the gas magnetic combined bearing of thrust bearing includes that the slot type gas magnetic combined bearing of above-mentioned magnetic bearing is Example, as shown in Figure 1, the end face towards the first stator 702 of thrust disc 701 or the first stator 702 towards thrust disc 701 The first dynamic pressure generation trough is provided on end face.

In the embodiment, when thrust disc 701 rotates, the flowing gas for being present in the first gap is pressed into the first dynamic pressure In generation trough, so that pressure is generated, to realize that thrust disc 701 is in axial direction non-contactly kept.Wherein, the first dynamic pressure is sent out The size that raw slot generates pressure is servo-actuated the difference of the angle for pressing generation trough, groove width, flute length, groove depth, slot number and flatness and becomes Change.In addition, the size that the first dynamic pressure generation trough generates pressure is also related with the rotation speed of thrust disc 701 and the first gap. It can be designed according to parameter of the actual condition to the first dynamic pressure generation trough.First dynamic pressure generation trough can be by forging, rolling Roll, etch or the modes such as punching press are formed on the first stator 702, alternatively, the first dynamic pressure generation trough can by forging, rolling, The modes such as etching or punching press are formed on thrust disc 701.

In the utility model embodiment, the first dynamic pressure generation trough can be set on pressure ring 709, for convenient for the first dynamic pressure hair The processing of raw slot, pressure ring 709 can be made of stainless steel material.

Optionally, as shown in Figures 6 to 9, the first dynamic pressure generation trough is radially or concentric circles are arranged, in this way, favorably In being more evenly distributed in air film in the first gap.

Optionally, the first dynamic pressure generation trough includes the first spiral groove and the second spiral groove, and the first helicla flute is surrounded on second Outside helicla flute, the spirals of the first spiral groove and the second spiral groove trend on the contrary, the first helicla flute close to the one of the second helicla flute It holds and is connected or disconnected with one end close to the first helicla flute of the second helicla flute.

Wherein, the distance in one end to the axle center of shaft 100 close to the second helicla flute of the first helicla flute is equal to the first spiral shell The distance of one end to the neighboring of the first stator 702 or thrust disc 701 close to the second helicla flute of spin slot.Alternatively, second The distance in one end to the axle center of shaft 100 close to the first helicla flute of helicla flute is equal to close first spiral of the second helicla flute The distance of one end of slot to the neighboring of the first stator 702 or thrust disc 701.

It, can be in shaft 100 by using the set-up mode of above-mentioned first dynamic pressure generation trough in the utility model embodiment In the case where rotating in the forward direction or reversely rotating, thrust disc 701 can be kept in a non-contact manner in the desired manner, to make to turn Axis 100 has the advantages that high load capacity and stability are good.

Optionally, the first stator 702 is provided with static pressure air inlet restriction hole 710, the one end in static pressure air inlet restriction hole 710 and the One gap communicates, and the other end connects external pressure gas source, for external pressure gas source to be delivered in the first gap.

It is the basis of slot type gas magnetic combined bearing in 702 side of the first stator of thrust bearing in the utility model embodiment On, by the way that above-mentioned static pressure air inlet restriction hole 710 is arranged, aerostatic bearing can be formed in the side, to form slot in the side Formula gas dynamic and static pressure-magnetic combined bearing.Wherein, the circulation diameter in static pressure air inlet restriction hole 710 can be real according to tolerance demand etc. Border operating condition is adjusted.

By above-mentioned setting, due to being provided with magnetic bearing 704 and aerostatic bearing simultaneously, the bearing capacity of thrust bearing into One step increases.Also, magnetic bearing 704 and aerostatic bearing can be mutually spare, wherein side's failure, failure or can not In the case where meeting unlocking condition, another party can be used as replacement bearing and serve the same role；For example, detecting magnetic bearing The case where 704 failure, control system control aerostatic bearing, which is opened, executes corresponding movement to substitute magnetic bearing 704, thus Improve the safety and reliability of thrust bearing.

Optionally, the first stator 702 is provided with multiple static pressure air inlet restrictions hole 710, and multiple static pressure air inlet restrictions hole 710 Along being provided at circumferentially spaced for the first stator 702.In this way, being conducive to keep the gas film pressure in the first gap more uniform.Preferably, Multiple static pressure air inlet restrictions hole 710 is arranged along the circumferential uniform intervals of the first stator 702.

Optionally, the distance in static pressure air inlet restriction hole 710 to the axle center of shaft 100 is more than or equal to static pressure air inlet restriction The distance of the neighboring of 710 to the first stator 702 of hole.

By above-mentioned setting, the aerostatic bearing of 702 side of the first stator of thrust bearing can be made more stable, if Static pressure air inlet restriction hole 710 then can not timely and effectively make air film be covered with entire thrust disc too close to the axle center of shaft 100 The end face of 701 the first stator 702 of direction, is not sufficiently stable the rotation of thrust disc 701.Preferably, static pressure air inlet restriction hole 710 Distance to the axle center of shaft 100 is equal to the distance of the neighboring of 710 to the first stator 702 of static pressure air inlet restriction hole.

On the other hand, with the gas magnetic combined bearing of thrust bearing for the paillon formula gas magnetic combined bearing comprising above-mentioned magnetic bearing For, as shown in Fig. 2, the first stator 702 further includes foil bearing 705, foil bearing 705 is set to magnetic bearing 704 and thrust Between disk 701, and there is the first gap between thrust disc 701, foil bearing 705 is provided with third magnetic part, paillon axis Holding 705 can be under the magneticaction between multiple first magnetic parts and third magnetic part in the axial direction of shaft 100 Upper movement, so that thrust disc 701 moves on the axial direction of shaft 100.

Optionally, foil bearing 705 includes:

The foil bearing seat being fixedly connected with magnetic bearing 704；

And it is set to the first paillon 7052 and the second paillon 7051 on foil bearing seat, the installation of the first paillon 7052 In on foil bearing seat, the second paillon 7051 is stacked at the side of the close thrust disc 701 of the first paillon 7052；

Wherein, the second paillon 7051 is flat paillon, and third magnetic part is set on the second paillon 7051, so that the second foil Piece 7051 can the axial direction under the magneticaction of multiple first magnetic parts and third magnetic part in shaft 100 move up It is dynamic；First paillon 7052 is the flexible deformation paillon that flexible deformation can occur when the second paillon 7051 is mobile.

Wherein, the material of foil bearing seat is non-magnetic material, preferably duralumin material.Pressure ring 709 in Fig. 2 can be used as Foil bearing seat.First paillon 7052 is flexible deformation paillon, it is contemplated that the material of permeability magnetic material is harder and crisp, should not be used as bullet Property deformation paillon, therefore, the preferred non-magnetic stainless steel band of the first paillon 7052.

In this way, by setting flat paillon for the second paillon 7051, convenient for the second paillon of control 7051 and thrust disc 701 it Between distance, in other words, convenient for control the first gap size；First paillon 7052 is using capableing of the paillon of flexible deformation, and one Aspect plays the role of connecting the second paillon 7051 and foil bearing seat, on the other hand may be implemented the second paillon 7051 relative to Foil bearing seat can be along the purpose of the axial movement of shaft 100.

Optionally, the first paillon 7052 is flexible deformation paillon wave-shaped, and the first paillon 7052 is not closed Annular which is provided with an opening, and one end of opening is fixing end, and fixing end is fixed on foil bearing seat, the other end of opening For movable end；

Wherein, the second paillon 7051 when moving on the axial direction of shaft 100, stretch by the ripple glaze on the first paillon 7052 Exhibition is shunk, and movable end is moved along the circumferential direction of annular.

In this way, by setting flexible deformation paillon wave-shaped for the first paillon 7052, convenient for utilizing ripple glaze Stretching, extension or shrinkage character push the second paillon 7051 to move on the axial direction of shaft 100.

It should be noted that the shape of the first paillon 7052 in the embodiment is not limited to wavy, Qi Taneng The shape for enough generating flexible deformation can be adapted for the first paillon 7052 in the embodiment.

Optionally, third magnetic part includes being set on a side surface of the close magnetic bearing 704 of the second paillon 7051 Magnetic material；

Wherein, magnetic material distribution in a strip shape on the second paillon 7051, and multiple strip magnetic portions are formed, multiple strips Magnetic portion is radially or circumferentially；

Alternatively, magnetic material is in spot distribution on the second paillon 7051.

Wherein, the preferred non-magnet material of material of the second paillon 7051 hides on the surface of the second paillon 7051 and sprays magnetic material After material, magnetic material can be covered with ceramic coating.Second paillon 7051 can be by using 40% zirconium oxide, 30% α Aluminium oxide and 30% magnesium aluminate spinels ceramic nano micro mist sintering be made.

If magnetic material is completely covered in the surface of the second paillon 7051, magnetic material and the first magnetic portion will increase dramatically The magnetic force generated between part is easy to cause the second paillon 7051 to deform in this way.In consideration of it, in the embodiment, by The surface of second paillon 7051 hides spray magnetic material, makes magnetic material distribution in a strip shape or dotted point on the second paillon 7051 Cloth can control the magnetic force generated between magnetic material and the first magnetic part in reasonable range, to avoid the second foil Piece 7051 deforms because of excessive magnetic force.

In the utility model embodiment, 703 side of the second stator of thrust bearing is gas bearing, can be gas dynamic pressure axis It holds, is also possible to aerostatic bearing, can also be gas dynamic and hydrostatic bearing.

On the one hand, by taking the gas bearing of thrust bearing is aero dynamic bearing as an example, as shown in Figures 6 to 9, thrust disc The end face of 701 the second stator 703 of direction, is moved alternatively, the end face towards thrust disc 701 of the second stator 703 is provided with second Press generation trough.

In the embodiment, when thrust disc 701 rotates, the flowing gas for being present in the second gap is pressed into the second dynamic pressure In generation trough, so that pressure is generated, to realize that thrust disc 701 is in axial direction non-contactly kept.Wherein, the second dynamic pressure is sent out The size that raw slot generates pressure is servo-actuated the difference of the angle for pressing generation trough, groove width, flute length, groove depth, slot number and flatness and becomes Change.In addition, the size that the second dynamic pressure generation trough generates pressure is also related with the rotation speed of thrust disc 701 and the second gap. It can be designed according to parameter of the actual condition to the second dynamic pressure generation trough.Second dynamic pressure generation trough can be by forging, rolling It rolls, etch or the modes such as punching press are formed on the second stator 703.

In the utility model embodiment, the other structures and set-up mode of the first dynamic pressure generation trough may be equally applied to second Dynamic pressure generation trough, and technical effect having the same do not repeat this to avoid repeating.

On the other hand, by taking the gas bearing of thrust bearing is aerostatic bearing as an example, the second stator 703 is provided with static pressure The one end in air inlet restriction hole 710, static pressure air inlet restriction hole 710 is communicated with the second gap, and the other end connects external pressure gas source, is used It is delivered in the second gap in by external pressure gas source.

Wherein, the circulation diameter in static pressure air inlet restriction hole 710 can be adjusted according to actual conditions such as tolerance demands.

Optionally, the second stator 703 is provided with multiple static pressure air inlet restrictions hole 710, and multiple static pressure air inlet restrictions hole 710 Along being provided at circumferentially spaced for the second stator 703.In this way, being conducive to keep the gas film pressure in the second gap more uniform.Preferably, Multiple static pressure air inlet restrictions hole 710 is arranged along the circumferential uniform intervals of the second stator 703.

Optionally, the distance in static pressure air inlet restriction hole 710 to the axle center of shaft 100 is more than or equal to static pressure air inlet restriction The distance of the neighboring of 710 to the second stator 703 of hole.

By above-mentioned setting, the aerostatic bearing of 703 side of the second stator of thrust bearing can be made more stable, if Static pressure air inlet restriction hole 710 then can not timely and effectively make air film be covered with entire thrust disc too close to the axle center of shaft 100 The end face of 701 the second stator 703 of direction, is not sufficiently stable the rotation of thrust disc 701.Preferably, static pressure air inlet restriction hole 710 Distance to the axle center of shaft 100 is equal to the distance of the neighboring of 710 to the second stator 703 of static pressure air inlet restriction hole.

On the other hand, by taking the gas bearing of thrust bearing is gas dynamic and hydrostatic bearing as an example, the direction second of thrust disc 701 The end face of stator 703 or the end face towards thrust disc 701 of the second stator 703 are provided with the second dynamic pressure generation trough, and second Stator 703 is provided with static pressure air inlet restriction hole 710, and the one end in static pressure air inlet restriction hole 710 is communicated with the second gap, and the other end connects External pressure gas source is connect, for external pressure gas source to be delivered in the second gap.

Optionally, the second stator 703 towards the inner peripheral surface of shaft 100 or second stator 703 of direction of shaft 100 Outer peripheral surface is provided with third dynamic pressure generation trough；And/or

The outer peripheral surface of the second stator 703 of direction of the inner peripheral surface or shaft 100 towards shaft 100 of second stator 703, It is provided with the 4th dynamic pressure generation trough.

In this way, action pneumatic will be formed in the gap between the first stator 702 and shaft 100 when shaft 100 is rotated Body, and/or, kinetic pressure gas will be formed in the gap between the second stator 703 and shaft 100, to realize thrust bearing in diameter Bearing capacity on direction, so that the thrust bearing in the utility model embodiment has the function of transverse bearing simultaneously, Further improve thrust bearing, dynamic property and stability especially under the state of running at high speed.

The thrust bearing of the utility model embodiment can be applied to following a variety of rotor-support-foundation systems.

In some embodiments, the rotor-support-foundation system that thrust bearing can be applied to flowering structure:

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

Motor, compressor and turbine are disposed in shaft；

At least two transverse bearings are additionally provided in shaft, at least two transverse bearings are contactless bearing；

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

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, when shaft is horizontally disposed with, the rotor-support-foundation system of the utility model embodiment is level Rotor-support-foundation system.When shaft is vertically arranged, the rotor-support-foundation system of the utility model embodiment is vertical rotor system.Below with level For rotor-support-foundation system (i.e. shaft is horizontally disposed), it is specifically described.

As shown in Figure 10 to Figure 12, rotor-support-foundation system includes:

The axis body of shaft 100, shaft 100 is structure as a whole, and shaft 100 is horizontally disposed；

Motor 200, compressor 300 and the turbine 400 being set in turn in shaft 100；

And it is set to thrust bearing 500, the first transverse bearing 600 and the second transverse bearing 700 in shaft 100, the One transverse bearing 600 is set to the side of the separate compressor 300 of motor 200, and the second transverse bearing 700 is set to compressor Between 300 and turbine 400.

Thrust bearing 500 is set between the first transverse bearing 600 and motor 200, as shown in Figure 10；Alternatively, thrust axis The side for the separate motor 200 that 500 are set to the first transverse bearing 600 is held, as shown in figure 11；Alternatively, thrust bearing 500 is arranged Between motor 200 and compressor 300, as shown in figure 12.

Wherein, when the quality of turbine 400 is larger, such as the material of turbine 400 is metal material, in order to make entire rotor The center of gravity of system, can be using real shown in Figure 10 or Figure 11 between the first transverse bearing 600 and the second transverse bearing 700 Apply mode.

And when the quality of turbine 400 is smaller, such as the material of turbine 400 is ceramic material or ceramic fibrous composite material Deng can use to make the center of gravity of entire rotor-support-foundation system between the first transverse bearing 600 and the second transverse bearing 700 Embodiment shown in Figure 12.

It should be noted that for embodiment shown in Figure 12, since thrust bearing 500 is set to motor 200 and pressure Between mechanism of qi 300, in order to avoid the thrust disc of thrust bearing 500 blocks the air inlet of compressor 300, embodiment party shown in Figure 12 Formula is suitable for the lesser thrust bearing 500 of thrust disk diameter.

In the utility model embodiment, the first transverse bearing 600 can use gas magnetic hybrid radial bearing or gas sound Press hybrid radial bearing.Second transverse bearing 700 is due to close to turbine 400, it is contemplated that the magnetic part in magnetic bearing can not be resistance to By 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, the side on turbine 400 close to the second transverse bearing 700 is provided with thermal insulation layer (not shown).Here, the material of thermal insulation layer can be aeroge or the good other materials of heat-proof quality.

Figure 13 to Figure 15 respectively illustrates the region of separate turbine 400 of the Figure 10 into Figure 12 on the second transverse bearing 700 The schematic diagram of magnetic part is set.

Compressor 300 can be centrifugal compressor 300, and 400 turbine of turbine can be centrifugal turbine；Motor 200 can be with The 5th dynamic pressure generation trough 201 has can be set in position for Hydrodynamic bearing electric machine, the bearing of the corresponding motor 200 of shaft 100.

As shown in Figure 16 to Figure 19, rotor-support-foundation system includes:

Motor 200, compressor 300 and the turbine 400 being set in turn in shaft 100；

And it is set to thrust bearing 500, the first transverse bearing 600, the second transverse bearing 700 and in shaft 100 Three transverse bearings 800, the first transverse bearing 600 are set to the side of the separate compressor 300 of motor 200, the second transverse bearing 700 are set between compressor 300 and turbine 400, and third transverse bearing 800 is set between motor 200 and compressor 300.

Thrust bearing 500 is set between the first transverse bearing 600 and motor 200, as shown in figure 16；Alternatively, thrust axis The side for the separate motor 200 that 500 are set to the first transverse bearing 600 is held, as shown in figure 17；Alternatively, thrust bearing 500 is arranged Between motor 200 and compressor 300, as shown in Figure 18 or Figure 19.

Due to increasing third transverse bearing 800, when thrust bearing 500 is set between motor 200 and compressor 300, Thrust bearing 500 both can be set between motor 200 and third transverse bearing 800, as shown in figure 18；Thrust bearing 500 is again It can be set between third transverse bearing 800 and compressor 300, as shown in figure 19.

By increasing third transverse bearing 800 between motor 200 and compressor 300, can further increase entire The stability of rotor-support-foundation system.

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, the side on turbine 400 close to the second transverse bearing 700 is provided with thermal insulation layer (not shown).Here, thermal insulation layer can be aeroge or other materials.

Figure 20 to Figure 23 respectively illustrates the region of separate turbine 400 of the Figure 16 into Figure 19 on the second transverse bearing 700 The schematic diagram of magnetic part is set.

As shown in figure 24, rotor-support-foundation system includes:

Motor 200, compressor 300 and the turbine 400 being set in turn in shaft 100；

And it is set to thrust bearing 500, the first transverse bearing 600, the second transverse bearing 700 and in shaft 100 Four transverse bearings 900, the first transverse bearing 600 are set to the side of the separate compressor 300 of motor 200, the second transverse bearing 700 are set between compressor 300 and turbine 400, and the 4th transverse bearing 900 is set to the separate compressor 300 of turbine 400 Side, thrust bearing 500 are set between compressor 300 and the second transverse bearing 700.

The utility model embodiment can be adapted for the excessive situation of 200 mass of motor, when the quality of motor 200 is excessive When, for the stability for keeping rotor-support-foundation system, the both ends of rotor-support-foundation system are required to setting transverse bearing (i.e. the first transverse bearing 600 With the 4th transverse bearing 900), while thrust bearing 500 is needed towards the movement of the side of turbine 400.

In view of the temperature of turbine 400 is higher, the magnetic part in magnetic bearing in thrust bearing 500 can not be resistant to turbine 400 high temperature transmitted, thrust bearing 500 can be set between compressor 300 and the second transverse bearing 700.Correspondingly, second Transverse bearing 700 can use gas hybrid transverse bearing.

In general, the temperature on turbine 400 close to 900 side of the 4th transverse bearing is higher than on turbine 400 close to the second diameter To the temperature of 700 side of bearing, therefore, the 4th transverse bearing 900 preferably uses gas hybrid transverse bearing.

Figure 25 shows showing for the region setting magnetic part of the separate turbine 400 in Figure 24 on the second transverse bearing 700 It is intended to.

It should be noted that thrust bearing 500 can be set radial in first when the quality of motor 200 is not too much big Between bearing 600 and motor 200；Alternatively, the separate motor 200 in first transverse bearing 600 can be set in thrust bearing 500 Side；Alternatively, thrust bearing 500 can be set between motor 200 and compressor 300.Due to being readily appreciated that, this is not made to have Body description.

As shown in figure 26, rotor-support-foundation system includes:

Motor 200, compressor 300 and the turbine 400 being set in turn in shaft 100；

And it is set to thrust bearing 500, the first transverse bearing 600, the second transverse bearing 700, in shaft 100 Three transverse bearings 800 and the 4th transverse bearing 900, the first transverse bearing 600 are set to the separate compressor 300 of motor 200 Side, the second transverse bearing 700 are set between compressor 300 and turbine 400, and third transverse bearing 800 is set to motor 200 Between compressor 300, the 4th transverse bearing 900 is set to the side of the separate compressor 300 of turbine 400, thrust bearing 500 It is set between compressor 300 and the second transverse bearing 700.

Increase third transverse bearing 800 between motor 200 and compressor 300, can be further improved entire rotor system The stability of system.

In the utility model embodiment, the second transverse bearing 700 and the 4th transverse bearing 900 can use gas sound Press hybrid radial bearing.

Figure 27 shows showing for the region setting magnetic part of the separate turbine 400 in Figure 26 on the second transverse bearing 700 It is intended to.

Shaft in horizontal rotor system shown in Figure 10 to Figure 27 is vertically arranged, it can be formed vertical turn corresponding Subsystem, to avoid repeating, the utility model embodiment does not repeat this.Vertical rotor system is in addition to that can reach and level The identical technical effect of rotor-support-foundation system, due to the vertical setting of rotor-support-foundation system, the center of gravity of all components is downward, additionally it is possible to avoid because turning Problem brought by cantilever axis structure caused by subsystem is horizontally disposed.

In some embodiments, thrust bearing can also be applied to the rotor-support-foundation system of flowering structure:

Motor, compressor, turbine and two transverse bearings are provided in shaft, two transverse bearings are contactless axis It holds；

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

Wherein, generator, thrust bearing and two transverse bearings are all set in the first casing, and compressor and turbine are all provided with It is placed in the second casing, the impeller of compressor and the impeller of turbine are in the second casing mutually by setting.

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.

In the utility model embodiment, the first casing and the second casing can be positioned and be connected by seam allowance (not shown) It connects, wherein thrust bearing and all transverse bearings can be provided entirely in the first casing (can be understood as generator casing) It is interior, 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 use in the first casing Machining accuracy in the position of setting bearing stator, it is logical for connecting the position of bearing stator in the first casing in assembly Crossing the processing that is once loaded can be completed, it is seen then that the utility model reduces the machining accuracy and assembly of Gas Turbine Generating Units Precision reduces costs, and is suitble to engineering batch production.

As shown in Figure 28 to Figure 30, rotor-support-foundation system includes:

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；

And first casing 801 and the second casing 901, the first casing 801 connect with the second casing 901, wherein motor 200, thrust bearing 500, the first transverse bearing 600 and the second transverse bearing 700 are all set in the first casing 801, compressor 300 and turbine 400 be all set in the second casing 901；The impeller of compressor 300 and the impeller of turbine 400 are in the second casing 901 Interior phase is by setting.

First transverse bearing 600 is set to the side far from the second casing 901 of motor 200, and the second transverse bearing 700 is set It is placed in the side close to the second casing 901 of motor 200.

Thrust bearing 500 is set between the first transverse bearing 600 and motor 200, as shown in figure 29；Alternatively, thrust axis It holds 500 to be set between motor 200 and the second transverse bearing 700, as shown in figure 30；Alternatively, thrust bearing 500 is set to second The side close to the second casing 901 of transverse bearing 700, as shown in figure 31.

It should be noted that for embodiment shown in Figure 31, since thrust bearing 500 is set to the second transverse bearing 700 side close to the second casing 901, that is to say, that thrust bearing 500 is disposed in proximity to calming the anger in the second casing 901 The position of machine, in order to avoid the thrust disc of thrust bearing 500 blocks the air inlet of compressor 300, embodiment shown in Figure 31 Suitable for the lesser thrust bearing 500 of thrust disk diameter.

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 system The center of gravity of system can be partial to 600 side of the first transverse bearing.In consideration of it, improving the bearing capacity of the second transverse bearing 700 facilitates Improve the stability of 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；The bearing of motor 200 can be hydrodynamic pressure bearing, and the position of the bearing of the corresponding motor 200 of shaft 100 can be set It is equipped with the 5th dynamic pressure generation trough 201.

Shaft in rotor-support-foundation system shown in Figure 28 to Figure 30 is vertically arranged, corresponding vertical rotor system can be formed System, to avoid repeating, the utility model embodiment does not repeat this.

It should be noted that thrust bearing 500 shown in Figure 10 to Figure 30 is pushing away in the utility model embodiment Power bearing.

The utility model embodiment also provides a kind of Gas Turbine Generating Units including any of the above-described kind of rotor-support-foundation system, under Face is specifically described with regard to the course of work of Gas Turbine Generating Units.

As previously shown, the thrust bearing in the utility model embodiment uses gas magnetic mixing thrust bearing, and transverse bearing can To use gas magnetic mixing thrust bearing or gas hybrid transverse bearing.For ease of description, we will not need shaft The bearing that 100 rotations can play lubricating action is defined as hydrostatic bearing, and shaft 100 turns to just workable when certain speed Bearing is defined as hydrodynamic bearing.Logic according to this, magnetic bearing and aerostatic bearing and gas in gas magnetic mixing thrust bearing Aerostatic bearing in hybrid transverse bearing is properly termed as hydrostatic bearing；And the gas in gas magnetic mixing thrust bearing Aero dynamic bearing in body hydrodynamic bearing and gas hybrid transverse bearing is properly termed as hydrodynamic bearing.

The utility model embodiment provides a kind of control method of Gas Turbine Generating Units, comprising:

S21, the hydrostatic bearing opened in transverse bearing and thrust bearing make so that shaft is moved to preset radial position The thrust disc of thrust bearing is moved to default axial position.

Wherein, opening hydrostatic bearing includes: the magnetic bearing in open bearing, and/or, the static pressure air inlet restriction into bearing Hole conveys gas.

S22, starting Gas Turbine Generating Units, air enter combustion chamber and the indoor fuel that burns after compressor compresses It is mixed and burned；The high temperature and high pressure gas of combustion chamber discharge impacts the turbine of turbine, rotates turbine, turbine passes through shaft Drive motor rotary electrification.

Below by taking motor is starting-generating integrated motor as an example, the start-up course of Gas Turbine Generating Units is specifically retouched It states.

After gas turbine controller (Electronic Control Unit, abbreviation ECU) receives enabling signal, to electricity Machine power controller (Data Processing Center, abbreviation DPC) sends motor drive mode instruction；DPC is switched to electricity The direct current of gas turbine internal battery is carried out frequency conversion, driving motor work by machine drive mode, DPC, and motor drives combustion gas wheel Machine promotes revolving speed.

After the revolving speed of gas turbine is promoted to fire speed, fuel valve is opened, into ignition procedure.Air is by air intake duct The high-temperature gas preheating for entering regenerator after being compressed into compressor and being discharged from turbine, the compressed air after preheating Combining combustion is mixed into combustion chamber and fuel, the high temperature and high pressure gas after the full combustion of combustion chamber enters turbine and rushes to turbine Hit, make turbine turbine rotate, turbine exhaust enter regenerator to enter combustion chamber before cold compression air preheating after by tail gas Pipe discharge, since turbine is connect with compressor and motor by shaft, the rotation of turbine turbine drives compressor to be rotated together to certainly Hold speed.

After gas turbine reaches self-sustain speed, DPC is hung up, and motor idle running continues growing throttle, and turbine continues to lift up power, Revolving speed is set to be promoted to working speed.ECU sends generator mode instruction to DPC；DPC is switched to generator mode, and by motor The alternating current of output passes through voltage and current needed for exporting user after rectifier transformer.

Wherein, compressor is centrifugal-flow compressor, which includes movable vane and stator blade circumferentially, quiet Leaf is diffuser.In this way, air detailed process that compressor is compressed is entered by air intake duct can be with are as follows: air enters centrifugal After the movable vane of compressor is compressed, compressed into diffuser (i.e. stator blade) continuation circumferentially.

Wherein, turbine turbine is centrifugal turbine, which is provided with movable vane.Combustor exit is circumferentially There is stator blade, which is nozzle.In this way, the high temperature and high pressure gas after the full combustion of combustion chamber enters turbine acting, make turbine whirlpool The detailed process for taking turns rotation can be with are as follows: high temperature and high pressure gas after the full combustion of combustion chamber passes through in combustor exit circumferentially cloth After the nozzle (i.e. stator blade) set carries out expansion acceleration, the movable vane of turbine is impacted, turbine is rotated.

S23, shaft revolving speed accelerate to after working speed, close the hydrostatic bearing in transverse bearing and thrust bearing.

Wherein, closing hydrostatic bearing includes: the magnetic bearing closed in bearing, and/or, stop the static pressure air inlet into bearing Throttle orifice conveys gas.

When S24, Gas Turbine Generating Units are shut down, the static pressure in the hydrostatic bearing and thrust bearing in transverse bearing is opened Bearing.

S25, shaft revolving speed be decelerated to after zero, close the hydrostatic bearing in transverse bearing and thrust bearing.

In above process, the bearing in rotor-support-foundation system is controlled, the hydrostatic bearing one in transverse bearing and thrust bearing is made The revolving speed of direct-open to shaft reaches working speed.

When Gas Turbine Generating Units are shut down, the bearing in rotor-support-foundation system is controlled, is made in transverse bearing and thrust bearing The always on revolving speed to shaft of hydrostatic bearing is zero.

The utility model embodiment provides the control method of another Gas Turbine Generating Units, comprising:

S31, the hydrostatic bearing opened in transverse bearing and thrust bearing make so that shaft is moved to preset radial position The thrust disc of thrust bearing is moved to default axial position.

S32, starting Gas Turbine Generating Units, air enter combustion chamber and the indoor fuel that burns after compressor compresses It is mixed and burned；The high temperature and high pressure gas of combustion chamber discharge impacts the turbine of turbine, rotates turbine, turbine passes through shaft Drive motor rotary electrification.

S33, shaft revolving speed accelerate to after the first preset value, close the static pressure axis in transverse bearing and thrust bearing It holds.

Wherein, the first preset value can be the 5% to 30% of rated speed.

Wherein, close hydrostatic bearing, comprising: close the magnetic bearing in bearing, and/or, stop static pressure into bearing into Moral discharge orifice conveys gas.

When S34, rotor-support-foundation system accelerate to single order critical speed or second order critical speed, transverse bearing and thrust bearing are opened In hydrostatic bearing.

S35, rotor-support-foundation system are steadily spent after single order critical speed or second order critical speed, and transverse bearing and thrust are closed Hydrostatic bearing in bearing.

In S36, Gas Turbine Generating Units stopping process, when rotor-support-foundation system is decelerated to single order critical speed or second order is critical When speed, the hydrostatic bearing in transverse bearing and thrust bearing is opened.

S37, rotor-support-foundation system are steadily spent after single order critical speed or second order critical speed, and transverse bearing and thrust are closed Hydrostatic bearing in bearing.

Revolving speed when being decelerated to the second preset value of S38, shaft, are opened in the hydrostatic bearing and thrust bearing in transverse bearing Hydrostatic bearing.

Wherein, the second preset value can be equal to the first preset value, can also be not equal to the first preset value, the second preset value can To be the 5% to 30% of rated speed.

S39, shaft revolving speed be decelerated to after zero, close the hydrostatic bearing in transverse bearing and thrust bearing.

In above process, before Gas Turbine Generating Units starting, the bearing in rotor-support-foundation system is controlled, transverse bearing is made It is opened with the hydrostatic bearing of thrust bearing.In this way, shaft under the action of the hydrostatic bearing of transverse bearing, is lifted up to default diameter To position；Thrust disc is pushed into default axial position under the action of the hydrostatic bearing of thrust bearing.

After Gas Turbine Generating Units starting, the revolving speed of shaft is gradually increased, and is preset when the revolving speed of shaft reaches first When value, for example, rated speed 5% to 30% when, control rotor-support-foundation system in bearing, make in transverse bearing and thrust bearing Hydrostatic bearing stops working.When the revolving speed of shaft reaches single order critical speed or second order critical speed, control in rotor-support-foundation system Bearing, reopen the hydrostatic bearing of transverse bearing and thrust bearing.The critical speed of single order is steadily spent in the revolving speed of shaft After degree or second order critical speed, the bearing in rotor-support-foundation system is controlled, makes hydrostatic bearing in transverse bearing and thrust bearing again It is secondary to stop working.

In Gas Turbine Generating Units stopping process, the revolving speed of shaft is gradually reduced, and is faced when the revolving speed of shaft reaches second order When boundary's speed or single order critical speed, the bearing in rotor-support-foundation system is controlled, makes the hydrostatic bearing of transverse bearing and thrust bearing again Secondary unlatching.After the revolving speed of shaft steadily spends second order critical speed or single order critical speed, the axis in rotor-support-foundation system is controlled It holds, the hydrostatic bearing in transverse bearing and thrust bearing is made to stop working again.When the revolving speed of shaft drops to predetermined value, example As rated speed 5% to 30% when, control rotor-support-foundation system in bearing, make the hydrostatic bearing of transverse bearing and thrust bearing again Secondary to open until revolving speed is reduced to after zero, the bearing in control rotor-support-foundation system makes the static pressure axis in transverse bearing and thrust bearing It holds and stops working again.

Below based on the control method of above-mentioned Gas Turbine Generating Units, the control method of rotor-support-foundation system is carried out specifically It is bright.

The utility model embodiment provides a kind of control method of rotor-support-foundation system, comprising:

S101, the hydrostatic bearing opened in transverse bearing and thrust bearing make so that shaft is moved to preset radial position The thrust disc of thrust bearing is moved to default axial position.

S102, shaft revolving speed accelerate to after working speed, close the hydrostatic bearing in transverse bearing and thrust bearing.

When S103, rotor-support-foundation system are shut down, the hydrostatic bearing in the hydrostatic bearing and thrust bearing in transverse bearing is opened.

S104, shaft revolving speed be decelerated to after zero, close the hydrostatic bearing in transverse bearing and thrust bearing.

In above process, before rotor-support-foundation system starting, the bearing in rotor-support-foundation system is controlled, transverse bearing and thrust axis are made The hydrostatic bearing held is opened.In this way, shaft under the action of the hydrostatic bearing of transverse bearing, is lifted up to preset radial position； Thrust disc is pushed into default axial position under the action of the hydrostatic bearing of thrust bearing.In transverse bearing and thrust bearing The always on revolving speed to shaft of hydrostatic bearing reach working speed.

When rotor-support-foundation system is shut down, the bearing in rotor-support-foundation system is controlled, the hydrostatic bearing in transverse bearing and thrust bearing is made The always on revolving speed to shaft is zero.

The utility model embodiment provides the control method of another rotor-support-foundation system, comprising:

S201, the hydrostatic bearing opened in transverse bearing and thrust bearing make so that shaft is moved to preset radial position The thrust disc of thrust bearing is moved to default axial position.

Wherein, hydrostatic bearing is opened, comprising: the magnetic bearing in open bearing, and/or, the static pressure air inlet section into bearing Discharge orifice conveys gas.

S202, shaft revolving speed accelerate to after the first preset value, close the static pressure axis in transverse bearing and thrust bearing It holds.

Wherein, the first preset value can be the 5% to 30% of rated speed.

When S203, rotor-support-foundation system accelerate to single order critical speed or second order critical speed, transverse bearing and thrust axis are opened Hydrostatic bearing in holding.

S204, rotor-support-foundation system are steadily spent after single order critical speed or second order critical speed, are closed transverse bearing and are pushed away Hydrostatic bearing in power bearing.

When S205, rotor-support-foundation system are decelerated to single order critical speed or second order critical speed, transverse bearing and thrust axis are opened Hydrostatic bearing in holding.

S206, rotor-support-foundation system are steadily spent after single order critical speed or second order critical speed, are closed transverse bearing and are pushed away Hydrostatic bearing in power bearing.

Revolving speed when being decelerated to the second preset value of S207, shaft, open the hydrostatic bearing and thrust bearing in transverse bearing In hydrostatic bearing.

S208, shaft revolving speed be decelerated to after zero, close the hydrostatic bearing in transverse bearing and thrust bearing.

In above process, before rotor-support-foundation system starting, the bearing in rotor-support-foundation system is controlled, transverse bearing and thrust axis are made The hydrostatic bearing held is opened.In this way, shaft under the action of the hydrostatic bearing of transverse bearing, is lifted up to preset radial position； Thrust disc is pushed into default axial position under the action of the hydrostatic bearing of thrust bearing.

After rotor-support-foundation system starting, the revolving speed of shaft is gradually increased, when the revolving speed of shaft reaches the first preset value, such as Rated speed 5% to 30% when, control rotor-support-foundation system in bearing, stop the hydrostatic bearing in transverse bearing and thrust bearing Only work.When the revolving speed of shaft reaches single order critical speed or second order critical speed, the bearing in rotor-support-foundation system is controlled, diameter is made It is reopened to the hydrostatic bearing of bearing and thrust bearing.Single order critical speed is steadily spent in the revolving speed of shaft or second order is critical After speed, the bearing in rotor-support-foundation system is controlled, the hydrostatic bearing in transverse bearing and thrust bearing is made to stop working again.

In rotor-support-foundation system stopping process, the revolving speed of shaft is gradually reduced, when the revolving speed of shaft reach second order critical speed or When single order critical speed, the bearing in rotor-support-foundation system is controlled, the hydrostatic bearing of transverse bearing and thrust bearing is again turned on.? The revolving speed of shaft is steadily spent after second order critical speed or single order critical speed, is controlled the bearing in rotor-support-foundation system, is made radial direction Hydrostatic bearing in bearing and thrust bearing stops working again.When the revolving speed of shaft drops to predetermined value, such as specified turn Speed 5% to 30% when, control rotor-support-foundation system in bearing, be again turned on the hydrostatic bearing of transverse bearing and thrust bearing directly After being reduced to zero to revolving speed, the bearing in rotor-support-foundation system is controlled, stops the hydrostatic bearing in transverse bearing and thrust bearing again Only work.

In conjunction with above content, it is clear that ground has understood the whole knot of the rotor-support-foundation system provided in the utility model embodiment Structure, using the overall structure of the Gas Turbine Generating Units of above-mentioned rotor-support-foundation system, the control methods of Gas Turbine Generating Units with And the control method of rotor-support-foundation system.

The utility model embodiment also provides a kind of control method of thrust bearing, below with the utility model embodiment The control method of thrust bearing (wherein, the first magnetic part in magnetic bearing is electromagnet) in rotor-support-foundation system carries out in detail Explanation.

As shown in figure 31, the utility model embodiment provides a kind of control method of thrust bearing, comprising:

S301: opening magnetic bearing, controls thrust disc under the magneticaction of multiple first magnetic parts in the axial direction of shaft It is moved on direction, so that the difference in the first gap and the second gap is less than or equal to predetermined value.

Wherein, the detailed process that magnetic bearing is opened are as follows: to the current signal of coil input predetermined value, thrust disc is in magnetic bearing Under the action of reach predetermined position between the first stator and the second stator.

S302: the revolving speed of the shaft accelerates to after working speed, closes the magnetic bearing.

S303: when the rotor-support-foundation system is shut down, the magnetic bearing is opened.

S304: the revolving speed of the shaft is decelerated to after zero, closes the magnetic bearing.

In above process, after magnetic bearing is opened, thrust disc reaches the first stator and second under the action of magnetic bearing to be determined The end face of predetermined position between son, thrust disc and the first stator and the second stator all has bearing clearance.

With the rotation of shaft, thrust disc opposite first stator and second in the case that air-flow lubricates in by bearing clearance Stator starts turning, to prevent from wearing.

As the revolving speed of shaft is increasing, the revolving speed of thrust disc is also synchronous to be increased, and is turned when the revolving speed of shaft reaches work When fast, (bearing clearance, that is, shape is arranged in the aero dynamic bearing of the thrust bearing between thrust disc and the first stator and the second stator At the aero dynamic bearing of the thrust bearing) generate gas film pressure can by thrust disc stablize, magnetic bearing can be closed at that time.

When rotor-support-foundation system is shut down, thrust disc slows down as shaft is slowed down, in order to stop shaft in entire rotor-support-foundation system It keeps stable during machine, magnetic bearing is opened when rotor-support-foundation system is shut down, magnetic can be closed after thrust disc stops completely Bearing.

As shown in figure 32, the utility model embodiment also provides the control method of another thrust bearing, comprising:

S401: opening magnetic bearing, controls thrust disc under the magneticaction of multiple first magnetic parts in the axial direction of shaft It is moved on direction, so that the difference in the first gap and the second gap is less than or equal to predetermined value；

S402: the revolving speed of the shaft accelerates to after the first preset value, closes the magnetic bearing.

S403: when the revolving speed of the shaft is decelerated to the second preset value, the magnetic bearing is opened.

S404: the revolving speed of the shaft is decelerated to after zero, closes the magnetic bearing.

As the revolving speed of shaft is increasing, the revolving speed of thrust disc is also synchronous to be increased, when the revolving speed of shaft reaches first in advance If value, for example, rated speed 5% to 30% when, aero dynamic bearing (thrust disc and the first stator and the of the thrust bearing It is to form the aero dynamic bearing of the thrust bearing that bearing clearance is arranged between two stators) gas film pressure that generates can be by thrust Disk is stablized, and can close magnetic bearing at that time.

In rotor-support-foundation system stopping process, thrust disc slows down as shaft is slowed down, when the revolving speed of shaft is pre- lower than second If value, for example, rated speed 5% to 30% when, at this point, the gas film pressure that generates of the aero dynamic bearing of thrust bearing also with Thrust disc slows down and reduces, and therefore, it is necessary to open magnetic bearing so that thrust disc keeps stablizing, after thrust disc stops completely i.e. Magnetic bearing can be closed.

Optionally, the above method further include:

When load is supported on the thrust disc, the thrust disc is under the action of load loads in the axial direction side of the shaft It moves up, when the difference in first gap and second gap is greater than the predetermined value, opens the magnetic bearing；

When the difference in first gap and second gap is less than or equal to the predetermined value, the magnetic is closed Bearing.

When load is supported on thrust disc, make the bearing clearance between thrust disc and the first stator or the second stator become smaller and Close to the side stator when, sensor (the preferred pressure sensor of sensor here) obtains the signal that air pressure increases, at this time magnetic Bearing needs to intervene work, and when thrust disc being made to reach new equilbrium position, magnetic bearing can stop working.

Optionally, when load is supported on the thrust disc, the thrust disc is under the action of load loads in the shaft Axial direction on move, when the difference in first gap and second gap is greater than the predetermined value, open the magnetic Bearing, comprising:

When load is supported on the thrust disc, the thrust disc is under the action of load loads in the axial direction side of the shaft It moves up, when the difference in first gap and second gap is greater than the predetermined value, controls the magnetic bearing with most High-power unlatching；Alternatively,

When load is supported on the thrust disc, the thrust disc is under the action of load loads in the axial direction side of the shaft Move up, when the difference in first gap and second gap is greater than the predetermined value, control the magnetic bearing according to Predeterminated frequency is opened in a manner of stroboscopic.

When there is external impact disturbance to occur, thrust disc may be rapidly close to certain side stator, it is likely that leads to the side Bearing clearance moment it is too small, make the local gas flow velocity of the side bearing gap location close to even up to velocity of sound, swash to cause 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 in sound Speed is remarkably decreased to its pressure when changing between subsonic speed in staged.In this case, need to control magnetic bearing with maximum work Rate is opened, or control magnetic bearing is opened in turn with predeterminated frequency, to provide the damping action to disturbance, to effectively inhibit external Disturbance.After thrust disc comes back to equilibrium state, magnetic bearing stops working.

It should be noted that in the utility model embodiment, for being provided with magnetic bearing and aerostatic bearing simultaneously In the case of, magnetic bearing and aerostatic bearing can be mutually spare, wherein side's failure, fail or be unable to satisfy open strip In the case where part, another party can be used as replacement bearing and serve the same role.For example, the case where detecting magnetic bearing failure Under, control external pressure gas source is opened to substitute magnetic bearing and execute corresponding movement, to improve the safety of bearing and reliable Property.

In the utility model embodiment, in the case where being provided with magnetic bearing and aerostatic bearing simultaneously, it can wrap Include the mode of being implemented as follows:

Open the magnetic bearing；And/or starting external pressure gas source, by static pressure air inlet restriction hole to the axis Hold gap location conveying gas；

The thrust disc is controlled under the magneticaction of the magnetic bearing and/or under the impetus of the gas in institute It states and is moved on the axial direction of shaft, so that the difference in first gap and second gap is less than or equal to described make a reservation for Value.

Wherein, it for opening the embodiment of magnetic bearing and aerostatic bearing simultaneously, can further increase practical The bearing capacity of the thrust bearing of new embodiment.

In above process, the advantages of facilitating real-time control using magnetic bearing, the unbalance mass, of active balancing thrust disc Or thrust disc whirling motion etc. leads to the factor of thrust disc over-deflection, and thrust disc is made to be fixed on a certain pole on the axial direction of shaft A small range.In addition, position (the i.e. linear velocity supersonic speed for generating shock wave can be accurately positioned in the accelerator of thrust disc Position), and by the size of current of control magnetic bearing and direction etc., so that magnetic bearing is generated opposite power to balance Shock Wave. After shock wave is steady, the control strategy of magnetic bearing is adjusted again, and thrust disc is fixed on a certain minimum model in a manner of most energy-efficient In enclosing.

In summary, the preferred embodiment in the utility model has the following beneficial effects:

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 in parallel 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, the thrust disc of bearing and stator can be made to rotate in bearing clearance with magnetic bearing, improve the low speed of bearing Performance extends 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 thrust bearing of power bearing, the utility model embodiment has the advantages that fast response time.

Third, 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.

In some embodiments, the transverse bearing in rotor-support-foundation system is paillon formula gas magnetic hybrid radial bearing.

About the concrete scheme of above-mentioned paillon formula gas magnetic hybrid radial bearing, may refer to application No. is Related description in the patent application document of CN201810030888.1, and identical beneficial effect can be reached, to avoid weight Multiple, the utility model embodiment does not repeat this.

In some embodiments, the transverse bearing in rotor-support-foundation system is slot type gas magnetic hybrid radial bearing.

As shown in Figure 33 to Figure 40, 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 the 6th 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.

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.

In the utility model embodiment, when shaft 100 rotates, the flowing gas for being present in the 4th gap 6203 is pressed into In 6th 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, the 6th dynamic pressure generation trough 6202 generates angle of the size with the 6th dynamic pressure generation trough 6202 of pressure, slot Width, flute length, groove depth, the difference of slot number and flatness and change.In addition, the 6th 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 the 6th dynamic pressure generation trough 6202 parameter is designed.6th 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.The material of 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 firmly Aluminum 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 the 6th dynamic pressure generation trough 6202 is set on 62016, for just In the processing of the 6th dynamic pressure generation trough 6202, second bearing set 62016 can be made of stainless steel material.Specifically, the 6th 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, the 6th dynamic pressure generation trough 6202 of mutually independent two parts；6th 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), the 6th dynamic pressure generation trough 6202 of mutually independent two parts.

Optionally, the 6th 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, the 6th 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 6th 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 to turn Axis 100 has the advantages that high load capacity and stability are good.6th dynamic pressure generation trough 6202, can be in addition to being set as V-shaped groove It is 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 The through-hole passed through；The second end of 4th sensor probe 62042 passes through the through-hole on the 4th magnetic bearing 6201, and extends between the 4th Gap 6203, and the side of the close shaft 100 of the second end end of the 4th sensor probe 62042 and the 4th magnetic bearing 6201 is flat Together.

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.

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, comprising:

S631, the 4th magnetic bearing is opened, controls shaft under the magneticaction of multiple 7th magnetic parts in the diameter of shaft It is moved on direction, pushes 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. The detailed process that 4th magnetic bearing is opened are as follows: 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, comprising:

S641, the 4th magnetic bearing is opened, controls shaft under the magneticaction of multiple 7th magnetic parts in the diameter of shaft It is moved on direction, pushes 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 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 second order critical speed, the 4th magnetic bearing, packet are opened It includes:

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

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

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

In S645, rotor-support-foundation system stopping process, when rotor-support-foundation system is decelerated to single order critical speed or second order critical speed, Open the 4th magnetic bearing.

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 second order critical speed, the 4th magnetic bearing, packet are opened It includes:

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

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

S646, rotor-support-foundation system are steadily spent after single order critical speed or second order critical speed, and the 4th magnetic bearing is closed.

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

S648, 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 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.

In the utility model embodiment, in the case where being provided with electromagnetic bearing and aerostatic bearing simultaneously, for " hydrostatic bearing in the transverse bearing is opened, so that the shaft is moved to preset radial position, " the step of, may include 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 institute State the 4th gap location conveying gas；

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

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 following beneficial effects:

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 thrust bearing, for being installed on shaft, which is characterized in that the thrust bearing includes:

Thrust disc, the thrust disc are fixedly connected in the shaft；

And it is arranged in the first stator and the second stator in the shaft, first stator and second stator difference Be set to the opposite sides of the thrust disc, between first stator and the thrust disc have the first gap, described second There is the second gap between stator and the thrust disc；

Wherein, first stator includes magnetic bearing, circumferentially arranged on the magnetic bearing to have multiple first magnetic parts, described Magnetic bearing can control the thrust disc and move on the axial direction of the shaft；Second stator and the thrust disc it Between constitute gas bearing.

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

It is provided with the second magnetic part on the thrust disc, the thrust disc can be in the multiple first magnetic part and described It is moved on the axial direction of the shaft under magneticaction between second magnetic part；

Second magnetic part includes the magnetic material being set on the end face towards first stator of the thrust disc；

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；

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

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

The magnetic bearing includes:

Magnetic bearing seat, the magnetic bearing seat are oppositely arranged with the thrust disc, on the magnetic bearing seat it is circumferentially arranged have it is multiple Holding tank, the multiple first magnetic part are set in the multiple holding tank, and the magnetic of the multiple first magnetic part Side where pole towards the thrust disc；

End cap and pressure ring, the end cap are set to the side far from the thrust disc of the magnetic bearing seat, the pressure ring setting In the side close to the thrust disc of the magnetic bearing seat, the end cap and the pressure ring cooperate, by the multiple first magnetic Property component is fixed on the magnetic bearing seat.

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

The multiple first magnetic part includes multiple permanent magnets, and the multiple permanent magnet is circumferentially set on the magnetic bearing It sets；

Alternatively, the multiple first magnetic part includes multiple electromagnet, the multiple electromagnet is on the magnetic bearing along week To setting, each electromagnet in the multiple electromagnet includes the magnetic core being set on the magnetic bearing and is wound in the magnetic Coil on core.

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

First stator is provided with first sensor, and the first sensor includes that first sensor lid and first sensor are visited The first end of head, the first sensor probe connects the first sensor lid, and the first sensor lid is fixed on described On magnetic bearing, the second end of the first sensor probe passes through the magnetic bearing and extends to first gap；And/or

Second stator is provided with second sensor, and the second sensor includes that second sensor lid and second sensor are visited The first end of head, the second sensor probe connects the second sensor lid, and the second sensor lid is fixed on described On second stator, the second end of the second sensor probe passes through second stator and extends to second gap.

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

First stator is set towards the end face of the thrust disc or the end face towards first stator of the thrust disc It is equipped with the first dynamic pressure generation trough；And/or

First stator is provided with the first static pressure air inlet restriction hole, the one end in the first static pressure air inlet restriction hole and described the One gap communicates, and the other end connects external pressure gas source, for external pressure gas source to be delivered in first gap.

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

Second stator is set towards the end face of the thrust disc or the end face towards second stator of the thrust disc It is equipped with the second dynamic pressure generation trough；And/or

Second stator is provided with the second static pressure air inlet restriction hole, the one end in the second static pressure air inlet restriction hole and described the Two gaps communicate, and the other end connects external pressure gas source, for external pressure gas source to be delivered in second gap.

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

The first dynamic pressure generation trough is radially or concentric circles are arranged；

The distance in axle center of the first static pressure air inlet restriction hole to the shaft is more than or equal to the first static pressure air inlet Throttle orifice to the neighboring of first stator distance.

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

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

The distance in axle center of the second static pressure air inlet restriction hole to the shaft is more than or equal to the second static pressure air inlet Throttle orifice to the neighboring of second stator distance.

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

First stator towards the inner peripheral surface of the shaft or the outer peripheral surface towards first stator of the shaft, It is provided with third dynamic pressure generation trough；And/or

Second stator towards the inner peripheral surface of the shaft or the outer peripheral surface towards second stator of the shaft, It is provided with the 4th dynamic pressure generation trough.

11. thrust bearing according to any one of claim 1 to 6, which is characterized in that

First stator further includes foil bearing, and the foil bearing is set between the magnetic bearing and the thrust disc, And there is first gap between the thrust disc, the foil bearing is provided with third magnetic part, the paillon axis Holding can be under the magneticaction between the multiple first magnetic part and the third magnetic part in the axis of the shaft It is moved on direction, so that the thrust disc moves on the axial direction of the shaft.

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

The foil bearing includes:

The foil bearing seat being fixedly connected with the magnetic bearing；

And it is set to the first paillon and the second paillon on the foil bearing seat, first paillon is installed on the foil On sheet bearing block, second paillon is stacked at the side close to the thrust disc of first paillon；

Wherein, second paillon is flat paillon, and the third magnetic part is set on second paillon, so that described the Two paillons can be under the magneticaction of the multiple first magnetic part and the third magnetic part in the axis of the shaft It is moved on direction；First paillon is the flexible deformation foil that flexible deformation can occur when second paillon is mobile Piece.

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

First paillon is flexible deformation paillon wave-shaped, and first paillon is not closed annular, is set thereon Have an opening, one end of the opening is fixing end, and the fixing end is fixed on the foil bearing seat, the opening it is another One end is movable end；

Wherein, ripple glaze stretching, extension of second paillon when being moved on the axial direction of the shaft, on first paillon Or shrink, the movable end is moved along the circumferential direction of the annular.

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

The third magnetic part includes the magnetism on a side surface of the magnetic bearing for being set to second paillon Material；

Wherein, magnetic material distribution in a strip shape on second paillon, and multiple strip magnetic portions are formed, it is the multiple Strip magnetic portion is radially or circumferentially；

Alternatively, the magnetic material is in spot distribution on second paillon.

15. a kind of rotor-support-foundation system, which is characterized in that the thrust axis including shaft and as described in any one of claims 1 to 14 It holds.

16. rotor-support-foundation system according to claim 15, 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；

At least two transverse bearings are additionally provided in the shaft, at least two transverse bearing is non-contact type bearing；

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.

17. rotor-support-foundation system according to claim 15, 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；

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, 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.